JP5899644B2 - Pulley device - Google Patents

Pulley device Download PDF

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Publication number
JP5899644B2
JP5899644B2 JP2011087210A JP2011087210A JP5899644B2 JP 5899644 B2 JP5899644 B2 JP 5899644B2 JP 2011087210 A JP2011087210 A JP 2011087210A JP 2011087210 A JP2011087210 A JP 2011087210A JP 5899644 B2 JP5899644 B2 JP 5899644B2
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outer ring
pulley
peripheral surface
convex portion
outer peripheral
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JP2012219936A (en
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康浩 石森
康浩 石森
昌大 喜多
昌大 喜多
磯　賢一
賢一 磯
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NSK Ltd
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NSK Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
    • 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
    • F16C35/067—Fixing them in a housing
    • 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
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/30—Material joints
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/63—Gears with belts and pulleys

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)
  • Pulleys (AREA)

Description

本発明は、合成樹脂製プーリに関し、例えば自動車用エンジンの補機或いはカムシャフトを駆動する為の無端ベルトやタイミングベルト（以下、単に「ベルト」とする。）に所望の張力を付与する為に、或いはベルトの巻き掛け角を確保すべくこのベルトを案内する為に使用するアイドラプーリとして利用するプーリ装置の改良に関する。   The present invention relates to a synthetic resin pulley, for example, for applying a desired tension to an endless belt or timing belt (hereinafter simply referred to as a “belt”) for driving an auxiliary machine of an automobile engine or a camshaft. Alternatively, the present invention relates to an improvement of a pulley device used as an idler pulley used to guide the belt so as to secure a winding angle of the belt.

従来から、自動車用エンジンの補機或いはカムシャフトを駆動する為のベルトに所望の張力を付与する等の為のアイドラプーリとして、転がり軸受の外周側に、鋼板等の金属板にプレス加工を施して造ったものを、この転がり軸受を構成する外輪に外嵌固定する状態で設けた所謂プレスプーリが広く使用されている。又、転がり軸受を構成する外輪の周囲に、この外輪の外周寄り部分をその内周側にモールドした状態で一体的に固設した合成樹脂製プーリも使用されている。特に、近年は、この合成樹脂製プーリが、アイドラプーリの軽量化及び低コスト化を図れると言った理由により、その採用が増加しつつある。   Conventionally, a metal plate such as a steel plate is pressed on the outer peripheral side of a rolling bearing as an idler pulley for applying a desired tension to a belt for driving an auxiliary machine of an automobile engine or a camshaft. A so-called press pulley is widely used in which a product made in such a manner is fitted and fixed to an outer ring constituting the rolling bearing. A synthetic resin pulley is also used which is integrally fixed around the outer ring constituting the rolling bearing in a state in which a portion near the outer periphery of the outer ring is molded on the inner peripheral side. In particular, in recent years, the use of synthetic resin pulleys is increasing due to the reason that the idler pulleys can be reduced in weight and cost.

例えば、特許文献１には、図８〜１１に示す様に、合成樹脂製のプーリ１を使用した張力付与装置２が記載されている。先ず、この張力付与装置２の構造に就いて、簡単に説明する。シリンダブロック等の固定の部分に結合固定するベースプレート３に形成した長孔４に沿う変位を自在とした支持軸５の基端部（図８の右端部）の頭部６に形成したねじ孔に、調整ボルト７の先端部を螺合させている。この調整ボルト７の基端部は、前記ベースプレート３の一端部（図８の上端部）に設けた折り曲げ板部８に形成した通孔９に挿通している。又、前記調整ボルト７の中間部でこの折り曲げ板部８よりも前記頭部６寄り部分には、調整ナット１０とロックナット１１とを螺合させている。   For example, Patent Document 1 describes a tension applying device 2 using a synthetic resin pulley 1 as shown in FIGS. First, the structure of the tension applying device 2 will be briefly described. In a screw hole formed in the head portion 6 of the base end portion (right end portion in FIG. 8) of the support shaft 5 that can be freely displaced along the long hole 4 formed in the base plate 3 coupled and fixed to a fixed portion such as a cylinder block. The tip of the adjustment bolt 7 is screwed together. The base end portion of the adjusting bolt 7 is inserted through a through hole 9 formed in a bent plate portion 8 provided at one end portion (upper end portion in FIG. 8) of the base plate 3. Further, an adjustment nut 10 and a lock nut 11 are screwed into a portion closer to the head 6 than the bent plate portion 8 in the intermediate portion of the adjustment bolt 7.

又、前記支持軸５には、支持スリーブ１２を介して、転がり軸受１３の内輪１４を支持している。単列深溝型のラジアル玉軸受であるこの転がり軸受１３の外輪１５の周囲には、合成樹脂製のプーリ１を固定している。このプーリ１は、互いに同心に設けられた内径側円筒部１６及び外径側円筒部１７を有する。この内径側円筒部１６の中間部外周面と外径側円筒部１７の中間部内周面とは、円輪状の連結部１８により連結しており、この連結部１８の両側面にそれぞれ複数本ずつの補強リブ１９、１９を、それぞれ放射状に設けている。   The support shaft 5 supports an inner ring 14 of a rolling bearing 13 via a support sleeve 12. A synthetic resin pulley 1 is fixed around the outer ring 15 of the rolling bearing 13 which is a single row deep groove type radial ball bearing. The pulley 1 has an inner diameter side cylindrical portion 16 and an outer diameter side cylindrical portion 17 provided concentrically with each other. The outer peripheral surface of the intermediate portion of the inner diameter side cylindrical portion 16 and the inner peripheral surface of the intermediate portion of the outer diameter side cylindrical portion 17 are connected by a ring-shaped connecting portion 18, and a plurality of both are provided on both side surfaces of the connecting portion 18. The reinforcing ribs 19 and 19 are provided radially.

この様なプーリ１は、前記内径側円筒部１６を深溝型の転がり軸受１３を構成する外輪１５の周囲に、図１１に示す様な射出成形用の金型２０により、この外輪１５の外周寄り部分をその内周側にモールドした状態で固設している。即ち、前記金型２０内に設けた、前記プーリ１の外形に対応した内形を有するキャビティ２１内に、図示しないゲートから溶融した熱可塑性樹脂を注入する。そして、この熱可塑性樹脂が冷却・固化した後に前記金型２０を開いて、前記プーリ１を前記転がり軸受１３と共に、前記キャビティ２１内から取り出す。   In such a pulley 1, the inner diameter side cylindrical portion 16 is placed around the outer ring 15 constituting the deep groove type rolling bearing 13 by an injection molding die 20 as shown in FIG. The portion is fixed in a state of being molded on the inner peripheral side. That is, molten thermoplastic resin is injected from a gate (not shown) into a cavity 21 provided in the mold 20 and having an inner shape corresponding to the outer shape of the pulley 1. After the thermoplastic resin is cooled and solidified, the mold 20 is opened, and the pulley 1 is taken out of the cavity 21 together with the rolling bearing 13.

上述の様なプーリ１を含んで構成する、前記張力付与装置２により、ベルトに所望の張力を付与するには、このベルトを、前記プーリ１の一部で、前記調整ナット１０と反対側周面（図８の下面）に掛け渡す。そして、前記調整ナット１０を回転させる事により前記プーリ１の位置を変えて、このプーリ１により前記ベルトに付与する張力を調節する。そして、この張力が所望値になった状態で、前記ロックナット１１を締め付け、前記プーリ１の位置を固定する。   In order to apply a desired tension to the belt by the tension applying device 2 configured to include the pulley 1 as described above, the belt is partly connected to the adjustment nut 10 on the opposite side of the pulley 1. It spans the surface (the lower surface in FIG. 8). Then, the position of the pulley 1 is changed by rotating the adjusting nut 10, and the tension applied to the belt by the pulley 1 is adjusted. Then, in a state where the tension reaches a desired value, the lock nut 11 is tightened to fix the position of the pulley 1.

上述の様なプーリ１を構成する合成樹脂は、前記転がり軸受１３の外輪１５を構成する金属材料よりも線膨張係数が大きい。この為、プーリ装置の使用時の温度上昇により、前記プーリ１と前記外輪１５との密着性が低下し、これらプーリ１と外輪１５との間で相対的な滑り（クリープ）が発生する可能性がある。クリープが発生すると、前記プーリ１の内周面が摩耗し、このプーリ１が前記外輪１５に対しがたついてしまう。この様な不都合の原因となるクリープを防止する為の技術として、例えば特許文献２に記載された技術がある。   The synthetic resin constituting the pulley 1 as described above has a larger linear expansion coefficient than the metal material constituting the outer ring 15 of the rolling bearing 13. For this reason, due to a temperature rise during use of the pulley device, the adhesion between the pulley 1 and the outer ring 15 may be reduced, and a relative slip (creep) may occur between the pulley 1 and the outer ring 15. There is. When creep occurs, the inner peripheral surface of the pulley 1 is worn, and the pulley 1 rattles against the outer ring 15. As a technique for preventing creep that causes such inconvenience, there is a technique described in Patent Document 2, for example.

図１２〜１３は、この特許文献２に記載されている、クリープを防止する為の従来構造の１例を示している。転がり軸受１３（図８〜１１参照）を構成する外輪１５ａの外周面に係止溝２２を設けており、この係止溝２２の底面に、ローレット加工による凹部２３、２３と凸部２４、２４とを全周に亙って交互に配置して成る、平目のローレット目２５を形成している。そして、前記外輪１５ａの係止溝２２の底面に形成した凹部２３、２３に、プーリ１ａを構成する合成樹脂の一部を進入・固化させる事で、このプーリ１ａの内周面に、それぞれが軸方向に長い突条２６、２６を形成している。これら各突条２６、２６と前記外輪１５ａのローレット目２５との係合により、前記プーリ１ａとこの外輪１５ａとの間でクリープが発生する事を防止している。   12 to 13 show an example of a conventional structure described in Patent Document 2 for preventing creep. A locking groove 22 is provided on the outer peripheral surface of the outer ring 15a constituting the rolling bearing 13 (see FIGS. 8 to 11). On the bottom surface of the locking groove 22, concave portions 23, 23 and convex portions 24, 24 by knurling are provided. Are alternately arranged over the entire circumference to form flat knurled eyes 25. And by making some synthetic resin which comprises the pulley 1a approach and solidify into the recessed parts 23 and 23 formed in the bottom face of the latching groove | channel 22 of the said outer ring | wheel 15a, each is carried out to the inner peripheral surface of this pulley 1a. Long ridges 26, 26 are formed in the axial direction. The engagement between each of the protrusions 26 and 26 and the knurled eye 25 of the outer ring 15a prevents the occurrence of creep between the pulley 1a and the outer ring 15a.

上述の様な特許文献２に記載された構造では、前記各突条２６、２６と前記外輪１５ａの外周面に形成されたローレット目２５との係合によりクリープが防止される。このクリープを防止する為、前記各突条２６、２６の基端部で、前記プーリ１ａと前記外輪１５ａとの間に加わるトルク（クリープ荷重）を支承する。前記特許文献２に記載された構造の場合、前記ローレット目２５の各凸部２４、２４の外径側円周方向両端縁の曲率半径ｒが小さい（曲率が大きい）為、前記各突条２６、２６の基端部に応力が集中する。そして、この応力が大きくなると、前記各突条２６、２６の基端部に亀裂等の損傷が発生する可能性がある。   In the structure described in Patent Document 2 as described above, the creep is prevented by the engagement between the protrusions 26 and 26 and the knurled eyes 25 formed on the outer peripheral surface of the outer ring 15a. In order to prevent this creep, a torque (creep load) applied between the pulley 1a and the outer ring 15a is supported at the base end portion of each of the protrusions 26 and 26. In the case of the structure described in Patent Document 2, since the radius of curvature r of the outer circumferential side end edges of the convex portions 24, 24 of the knurled eye 25 is small (the curvature is large), the protrusions 26 , 26 concentrates stress at the base end. And when this stress becomes large, damages, such as a crack, may occur in the base end part of each said protrusion 26,26.

又、前記特許文献２に記載された構造では、前記ローレット目２５を前記外輪１５ａの外周面のうち、軸方向中間部２箇所位置に設けている。この外輪１５ａの軸方向中間部は、内周面に外輪軌道２７（図１０参照）を形成している為、肉薄となっている。この為、前記ローレット目２５の凹部２３、２３の径方向の深さ寸法を確保する事が難しく、使用時の温度上昇の程度によっては、前記各突条２６、２６と前記ローレット目２５との係合が外れ、前記プーリ１と前記外輪１５とのクリープを防止できなくなる可能性がある。   Moreover, in the structure described in the said patent document 2, the said knurled eyes 25 are provided in the axial direction intermediate part 2 location position among the outer peripheral surfaces of the said outer ring | wheel 15a. Since the outer ring raceway 27 (see FIG. 10) is formed on the inner peripheral surface, the axially intermediate portion of the outer ring 15a is thin. For this reason, it is difficult to secure the radial depth of the recesses 23, 23 of the knurled eye 25, and depending on the degree of temperature rise during use, the protrusions 26, 26 and the knurled eye 25 There is a possibility that the engagement is disengaged and the creep between the pulley 1 and the outer ring 15 cannot be prevented.

特開平１０−１２２３３９号公報JP-A-10-122339 特開平１１−１４８５５０号公報Japanese Patent Laid-Open No. 11-148550

本発明は、上述の様な事情に鑑みて、使用時の温度上昇によってプーリと転がり軸受の外輪との密着性が低下しても、これらプーリと外輪との間のクリープ発生を防止できる構造に於いて、このプーリの一部にクリープ荷重による応力が集中してこのプーリが破損する事を防止できるプーリ装置を実現すべく発明したものである。   In view of the circumstances as described above, the present invention has a structure capable of preventing the occurrence of creep between the pulley and the outer ring even when the adhesion between the pulley and the outer ring of the rolling bearing is reduced due to a temperature rise during use. However, the present invention has been invented to realize a pulley apparatus capable of preventing the pulley from being damaged due to concentration of a stress due to a creep load on a part of the pulley.

本発明のプーリ装置は、プーリと転がり軸受とを備える。
このうちのプーリは、合成樹脂製で外周面にベルトを掛け渡す。
又、前記転がり軸受は、前記プーリの内径側に保持されており、外周面に単列深溝型の内輪軌道を有する内輪と、内周面に単列深溝型の外輪軌道を有する外輪と、これら内輪軌道と外輪軌道との間に転動自在に設けられた複数個の玉とを備える。そして、前記外輪を前記プーリの内径側に、このプーリの射出成型時にモールドする事で、保持固定している。 The pulley device of the present invention includes a pulley and a rolling bearing.
Of these, the pulley is made of synthetic resin, and the belt is wound around the outer peripheral surface.
Further, the rolling bearing is held on the inner diameter side of the pulley, an inner ring having a single row deep groove type inner ring raceway on an outer peripheral surface, an outer ring having a single row deep groove type outer ring raceway on an inner peripheral surface, A plurality of balls are provided between the inner ring raceway and the outer ring raceway so as to be freely rollable. The outer ring is held and fixed on the inner diameter side of the pulley by molding at the time of injection molding of the pulley.

特に、本発明のプーリ装置に於いては、前記転がり軸受の外輪の外周面の軸方向の一部に、ローレット加工による凹部と凸部とを全周に亙って交互に配置して成る平目のローレット目を形成している。そして、これら各凸部の外径側円周方向両端縁に、断面円弧形（Ｒ状）の面取り部を形成している。
又、本発明の場合には、追加的に、前記ローレット目を、前記外輪の外周面の軸方向の一部に形成された第一ローレット目と、この外輪の外周面のうち、内周面に前記外輪軌道を形成した部分から軸方向に外れた肉厚部に形成された第二ローレット目とから構成しており、前記凸部を、前記外輪の外周面の軸方向の一部に形成された第一凸部と、前記肉厚部に形成された第二凸部とから構成している。そして、前記第一ローレット目を、それぞれ複数ずつの第一凹部と前記第一凸部とを、円周方向に関して交互に配置したものとし、前記第二ローレット目を、それぞれ複数の前記第一凹部と前記第二凸部と、これら各第一凹部から円周方向に外れた位置に設けられて、これら各第一凹部よりも大きな深さ寸法を有する、少なくとも１個の第二凹部とを備えたものとしている。これにより、前記第一凸部及び前記第二凸部の外径側円周方向両端縁に面取り部を形成している。 In particular, in the pulley device of the present invention, a flat surface formed by alternately arranging concave and convex portions by knurling on the entire circumference of a part of the outer peripheral surface of the outer ring of the rolling bearing. The knurled eyes are formed. Then, a chamfered portion having an arcuate cross section (R shape) is formed at both circumferential edges on the outer diameter side of each convex portion.
Further, in the case of the present invention, in addition, the knurled eye, the first knurled eye formed on a part of the outer peripheral surface of the outer ring in the axial direction, and the outer peripheral surface of the outer ring, the inner peripheral surface And a second knurled portion formed in a thick portion deviated in the axial direction from the portion where the outer ring raceway is formed, and the convex portion is formed in a part of the outer peripheral surface of the outer ring in the axial direction. It is comprised from the made | formed 1st convex part and the 2nd convex part formed in the said thick part. And each said 1st knurled eye shall be arranged alternately about a plurality of 1st crevices and said 1st convex part about the circumference direction, and said 2nd knurled eyes are a plurality of said 1st crevice, respectively. And the second convex part, and at least one second concave part provided at a position deviated in the circumferential direction from each of the first concave parts and having a depth dimension larger than each of the first concave parts. It is assumed. Thereby, the chamfered part is formed in the outer diameter side circumferential direction both ends edge of said 1st convex part and said 2nd convex part.

上述の様に構成する本発明のプーリ装置の場合には、使用時の温度上昇により、プーリと転がり軸受の外輪との密着性が低下しても、このプーリの内周面とこの外輪の外周面に形成されたローレット目との係合により、これらプーリと外輪との間のクリープを防止できる。
又、各凸部（第一凸部及び第二凸部）の外径側円周方向両端縁に断面円弧形の面取り部を設けている為、使用時に、前記プーリの内周面のうち、クリープ荷重を支承する部分である、前記各凸部の基端部に加わる応力を緩和して、これら各凸部の基端部に亀裂等の損傷が発生する事を防止できる。 In the case of the pulley device of the present invention configured as described above, even if the adhesion between the pulley and the outer ring of the rolling bearing decreases due to temperature rise during use, the inner peripheral surface of the pulley and the outer periphery of the outer ring By engagement with the knurled eyes formed on the surface, creep between these pulleys and the outer ring can be prevented.
In addition, since chamfered portions having a circular arc cross section are provided at both circumferential edges on the outer diameter side of each convex portion (the first convex portion and the second convex portion) , during use, of the inner peripheral surface of the pulley The stress applied to the base end portion of each convex portion, which is a portion that supports the creep load, can be relaxed, and damage such as cracks can be prevented from occurring at the base end portion of each convex portion.

本発明に関する参考例の１例を示す、外輪のみを径方向から見た部分正面図。 The partial front view which looked at the outer ring only from the radial direction which shows one example of the reference example regarding this invention . 外輪の周囲に合成樹脂製のプーリを装着した状態で示す、図１の部分拡大ａ−ａ断面図。FIG. 2 is a partial enlarged aa cross-sectional view of FIG. 1 showing a synthetic resin pulley mounted around an outer ring. 合成樹脂製のプーリを未装着の状態で示す、図１の部分拡大ｂ−ｂ断面図。The partial expanded bb sectional drawing of FIG. 1 which shows the synthetic resin pulley in the state which has not mounted | worn. 本発明の実施の形態の第１例を示す、図１と同様の図。The figure similar to FIG. 1 which shows the 1st example of embodiment of this invention. 外輪の周囲に合成樹脂製のプーリを装着した状態で示す、図４の部分拡大ｃ−ｃ断面図。FIG. 5 is a partially enlarged cross-sectional view taken along the line cc in FIG. 4 in a state where a synthetic resin pulley is mounted around the outer ring. 合成樹脂製のプーリを未装着の状態で示す、図４の部分拡大ｄ−ｄ断面図。FIG. 6 is a partially enlarged dd cross-sectional view of FIG. 4 showing a synthetic resin pulley not attached. 本発明の実施の形態の第２例を示す、図１と同様の図。The figure similar to FIG. 1 which shows the 2nd example of embodiment of this invention. プーリ装置を組み込んだ張力付与装置を示す断面図。Sectional drawing which shows the tension | tensile_strength provision apparatus incorporating the pulley apparatus. プーリ装置を取り出して図８の側方から見た状態で示す正面図。The front view shown in the state which took out the pulley apparatus and was seen from the side of FIG. 同じく部分切断斜視図。Similarly a partially cut perspective view. プーリを射出成形する金型を、補強リブから外れた部分で切断した状態で示す部分断面図（Ａ）と、補強リブ部分で切断した状態で示す部分断面図（Ｂ）。The fragmentary sectional view (A) shown in the state where the metal mold | die which injection-molds a pulley was cut | disconnected in the part remove | deviated from the reinforcement rib, and the fragmentary sectional view (B) shown in the state cut | disconnected by the reinforcement rib part. 従来構造に係るプーリ装置の要部断面図。Sectional drawing of the principal part of the pulley apparatus which concerns on the conventional structure. 図１２のｅ−ｅ断面図。Ee sectional drawing of FIG.

［本発明に関する参考例］
図１〜３は、本発明に関する参考例の１例を示している。尚、本参考例を含めて、本発明の特徴は、プーリと外輪とのクリープを確実に防止すると共に、このプーリの一部にクリープ荷重による応力が集中してこのプーリが破損する事の防止を図れるプーリ装置を実現する点にある。その他の部分の構造及び作用は、前述の図８〜１１に示した構造を含め、従来から知られているプーリ装置と同様であるから、同等部分に関する図示並びに説明は、省略又は簡略にし、以下、本参考例の特徴部分を中心に説明する。 [ Reference Example for the Present Invention ]
1 to 3 show an example of a reference example related to the present invention . The features of the present invention, including this reference example , reliably prevent the pulley and the outer ring from creeping, and prevent the pulley from being damaged due to the concentration of stress due to the creep load on a part of the pulley. It is in the point which implement | achieves the pulley apparatus which can plan. Since the structure and operation of the other parts are the same as those of a conventionally known pulley apparatus including the structure shown in FIGS. 8 to 11 described above, the illustration and description of the equivalent parts are omitted or simplified. The description will focus on the features of this reference example .

本参考例の場合、転がり軸受１３（図８〜１１参照）を構成する外輪１５ｂの外周面のうち、内周面に外輪軌道２７ａを形成した部分から軸方向に外れた肉厚部２８に、全周に亙って係止溝２２ａを設けている。そして、この係止溝２２ａの底面に、ローレット加工による第一凹部２９、２９と凸部３０、３０と第二凹部３１、３１とを全周に亙って繰り返し順番に（第一凹部２９→凸部３０→第二凹部３１→凸部３０の順番で繰り返し）配置して成る、平目のローレット目２５ａを形成している。尚、図示の例では、前記各部２９、３０、３１を繰り返し順番に配置しているが、必ずしもこの様に配置する必要はない。
このローレット目２５ａの第二凹部３１の径方向の深さ寸法ｈ３１は、第一凹部２９の径方向の深さ寸法ｈ２９よりも大きく（ｈ３１＞ｈ２９）、１．２〜２．５倍（１．２≦ｈ３１／ｈ２９≦２．５）としている。前記深さ寸法ｈ３１が、前記深さ寸法ｈ２９の１．２倍よりも小さい場合には、使用時の温度上昇によるクリープ防止効果を十分に得る事ができない。又、前記深さ寸法ｈ３１が、前記深さ寸法ｈ２９の２．５倍よりも大きい場合には、前記ローレット目２５ａをローレット加工により形成する事が難しくなる。 In the case of this reference example , in the outer peripheral surface of the outer ring 15b constituting the rolling bearing 13 (see FIGS. 8 to 11), the thick portion 28 that is axially deviated from the portion where the outer ring raceway 27a is formed on the inner peripheral surface, A locking groove 22a is provided over the entire circumference. Then, on the bottom surface of the locking groove 22a, the first concave portions 29, 29, the convex portions 30, 30 and the second concave portions 31, 31 by knurling are repeated in order over the entire circumference (first concave portion 29 → A flat knurled eye 25a is formed, which is repeatedly arranged in the order of convex portion 30 → second concave portion 31 → convex portion 30). In the example shown in the figure, the respective parts 29, 30, 31 are arranged repeatedly in order, but it is not always necessary to arrange them in this manner.
The radial depth dimension h 31 of the second recess 31 of the knurled eye 25a is larger than the radial depth dimension h 29 of the first recess 29 (h 31 > h 29 ), and 1.2-2. Five times (1.2 ≦ h 31 / h 29 ≦ 2.5). When the depth dimension h 31 is smaller than 1.2 times the depth dimension h 29 , the effect of preventing creep due to the temperature rise during use cannot be obtained sufficiently. Further, when the depth dimension h 31 is larger than 2.5 times the depth dimension h 29 , it is difficult to form the knurled eye 25 a by knurling.

又、前記各凸部３０、３０の外径側円周方向両端縁のうち、前記各第一凹部２９、２９側端縁には、断面円弧形のＲ面取り部３２を、前記各第二凹部３１、３１側端縁には、同じくＲ面取り部３３を、それぞれ設けている。前記第一、第二各凹部２９、３１の径方向の深さ寸法ｈ２９、ｈ３１に対する前記各Ｒ面取り部３２、３３の断面の曲率半径ｒ３２、ｒ３３の割合は、それぞれ前記各凹部２９、３１の径方向の深さ寸法ｈ２９、ｈ３１の２５〜５０％（０．２５≦ｒ３２／ｈ２９≦０．５、０．２５≦ｒ３３／ｈ３１≦０．５）としている。前記各曲率半径ｒ３２、ｒ３３が、それぞれ前記各深さ寸法ｈ２９、ｈ３１の２５％よりも小さい場合には、プーリ１ｂが前記外輪１５ｂに対し相対回転（クリープ）する傾向になった時、このプーリ１ｂのうち、後述する第一、第二各突条３４、３５の基端部に応力が集中し、亀裂等の損傷が発生する事を十分に防止できない。前記各曲率半径ｒ３２、ｒ３３が、それぞれ前記各深さ寸法ｈ２９、ｈ３１の５０％よりも大きい場合には、前記各Ｒ面取り部３２、３３部分で前記外輪１５ｂに対して前記プーリ１ｂが滑り易くなり、クリープ防止効果を十分に得る事ができない。
又、図示は省略するが、前記ローレット目２５ａの表面には、ディンプル加工により多数の微小凹部を形成している。 Further, out of both circumferential edges on the outer diameter side of each convex portion 30, 30, the first concave portion 29, 29 side edge is provided with an R-chamfered portion 32 having an arcuate cross section at each second end. Similarly, an R chamfered portion 33 is provided at each of the end edges of the recesses 31 and 31. The ratios of the curvature radii r 32 and r 33 of the cross-sections of the R chamfered portions 32 and 33 to the radial depth dimensions h 29 and h 31 of the first and second concave portions 29 and 31 are the respective concave portions. 29 to 31 in the radial depth dimension h 29 , 25 to 50% of h 31 (0.25 ≦ r 32 / h 29 ≦ 0.5, 0.25 ≦ r 33 / h 31 ≦ 0.5) Yes. When the respective curvature radii r 32 and r 33 are smaller than 25% of the respective depth dimensions h 29 and h 31 , the pulley 1b tends to rotate (creep) relative to the outer ring 15b. At this time, in the pulley 1b, it is not possible to sufficiently prevent the stress from concentrating on the base end portions of the first and second protrusions 34 and 35 to be described later and causing damage such as cracks. When the respective curvature radii r 32 and r 33 are larger than 50% of the respective depth dimensions h 29 and h 31 , the pulleys with respect to the outer ring 15b at the respective R chamfered portions 32 and 33 are provided. 1b becomes slippery and the effect of preventing creep cannot be sufficiently obtained.
Although not shown, a large number of minute recesses are formed on the surface of the knurled eye 25a by dimple processing.

本参考例のプーリ装置では、前記外輪１５ｂの径方向外側に合成樹脂製のプーリ１ｂを射出成形により設けた（モールド成形した）状態で、前記係止溝２２ａの底面に形成した前記各第一凹部２９、２９と前記各第二凹部３１、３１とに、前記プーリ１ｂを構成する合成樹脂の一部が進入・固化する。そして、このプーリ１ｂの内周面に、第一突条３４、３４及び第二突条３５、３５をそれぞれ形成している。又、前記合成樹脂の一部は、前記ローレット目２５ａの表面に形成した微小凹部にも進入・固化する事で、前記プーリ１ｂの内周面の一部に微小凸部を形成している。 In the pulley device of the present reference example , the first each formed on the bottom surface of the locking groove 22a in a state where the synthetic resin pulley 1b is provided by injection molding on the radially outer side of the outer ring 15b (molded). Part of the synthetic resin constituting the pulley 1b enters and solidifies into the recesses 29 and 29 and the second recesses 31 and 31, respectively. And the 1st protrusion 34,34 and the 2nd protrusion 35,35 are formed in the internal peripheral surface of this pulley 1b, respectively. Further, a part of the synthetic resin also enters and solidifies into a minute recess formed on the surface of the knurled eye 25a, thereby forming a minute projection on a part of the inner peripheral surface of the pulley 1b.

上述の様に構成する本参考例のプーリ装置の場合には、前記ローレット目２５ａの各第一凹部２９、２９と前記プーリ１ｂの第一突条３４、３４との係合により、前記外輪１５ｂとこのプーリ１ｂとのクリープを防止できる。更に、この外輪１５ｂのローレット目２５ａの表面に形成された微小凹部と前記プーリ１ｂの内周面のうち一部の表面に形成された微小凸部との係合によってもクリープを防止できる。 In the case of the pulley device of the present reference example configured as described above, the outer ring 15b is engaged by the engagement between the first recesses 29 and 29 of the knurled eye 25a and the first protrusions 34 and 34 of the pulley 1b. And creep with this pulley 1b can be prevented. Further, the creep can be prevented by the engagement between the minute concave portion formed on the surface of the knurled eye 25a of the outer ring 15b and the minute convex portion formed on a part of the inner peripheral surface of the pulley 1b.

又、前記ローレット目２５ａの凸部３０、３０の外径側円周方向両端縁に、断面円弧状のＲ面取り部３２、３３をそれぞれ形成している。即ち、前述の特許文献２に記載された構造よりも前記各凸部３０、３０の外径側円周方向両端縁の曲率半径ｒ３２、ｒ３３を大きく（曲率が小さく）している。従って、前記プーリ１ｂが前記外輪１５ｂに対し相対回転（クリープ）する傾向になり、前記各突条３４、３５に、円周方向の力が加わった場合でも、これら各突条３４、３５の基端部に応力が集中する事を防止できる。この結果、前記円周方向の力が大きくなっても、前記各突条３４、３５の基端部に亀裂等の損傷が発生する事を防止できる。 Further, R chamfered portions 32 and 33 each having an arcuate cross section are formed at both ends of the convex portions 30 and 30 of the knurled eye 25a in the circumferential direction. In other words, the radii of curvature r 32 and r 33 at the outer circumferential side circumferential edges of the convex portions 30 and 30 are larger (the curvature is smaller) than the structure described in Patent Document 2 described above. Accordingly, the pulley 1b tends to rotate (creep) relative to the outer ring 15b, and even when a circumferential force is applied to each of the protrusions 34 and 35, the base of each of the protrusions 34 and 35 is increased. It is possible to prevent stress from concentrating on the end. As a result, even if the circumferential force increases, it is possible to prevent damage such as cracks from occurring at the base ends of the protrusions 34 and 35.

又、本参考例の構造の場合、前記ローレット目２５ａの第二凹部３１の径方向の深さ寸法ｈ３１は、前記第一凹部２９の同寸法ｈ２９よりも大きい。この為、使用時の温度上昇が大きくなり、前記プーリ１ｂの各第一突条３４、３４と前記ローレット目２５ａの各第一凹部２９、２９との係合によっては、前記プーリ１ｂと前記外輪１５ｂとのクリープが防止できなくなった場合にも、このプーリ１ｂの各第二突条３５、３５と前記ローレット目２５ａの各第二凹部３１、３１との係合により、前記プーリ１ｂと前記外輪１５ｂとのクリープを防止できる。 In the case of the structure of the present reference example , the radial depth h 31 of the second recess 31 of the knurled eye 25 a is larger than the same dimension h 29 of the first recess 29. For this reason, the temperature rise during use increases, and depending on the engagement between the first protrusions 34, 34 of the pulley 1b and the first recesses 29, 29 of the knurled eye 25a, the pulley 1b and the outer ring Even when the creep with the pulley 15b cannot be prevented, the pulley 1b and the outer ring are engaged with the second protrusions 35, 35 of the pulley 1b and the second recesses 31, 31 of the knurled eye 25a. Creeping with 15b can be prevented.

［実施の形態の第１例］
図４〜６は、請求項１に対応する、本発明の実施の形態の第１例を示している。本例の場合、転がり軸受１３（図８〜１１参照）を構成する外輪１５ｃの外周面に設けた係止溝２２ｂの軸方向寸法を、上述した参考例よりも大きくしている。即ち、前記外輪１５ｃのうち、内周面に外輪軌道２７ａを形成した部分から軸方向に外れた肉厚部２８だけでなく、この内周面に外輪軌道２７ａを形成した部分である肉薄部３６の端部にも、前記係止溝２２ｂの一部を形成している。 [ First example of embodiment]
4 to 6 show a first example of an embodiment of the present invention corresponding to claim 1 . In the case of this example, the axial dimension of the locking groove 22b provided on the outer peripheral surface of the outer ring 15c constituting the rolling bearing 13 (see FIGS. 8 to 11) is made larger than that of the reference example described above. That is, in the outer ring 15c, not only the thick portion 28 axially deviated from the portion where the outer ring raceway 27a is formed on the inner peripheral surface, but also the thin portion 36 which is the portion where the outer ring raceway 27a is formed on the inner peripheral surface. A part of the locking groove 22b is also formed at the end portion.

そして、前記係止溝２２ｂの底面のうち、前記肉薄部３６に形成された部分に、ローレット加工による第一凹部２９ａ、２９ａと第一凸部３７、３７とを全周に亙って交互に配置して成る、平目の第一ローレット目３８を形成している。更に、前記係止溝２２ｂの軸方向のうち、前記肉厚部２８に形成された部分にだけ、ローレット加工による第一凹部２９ａ、２９ａと第二凸部３９、３９と第二凹部３１ａ、３１ａとを全周に亙って繰り返し順番に（第一凹部２９ａ→第二凸部３９→第二凹部３１ａ→第二凸部３９の順番で繰り返し）配置して成る、平目の第二ローレット目４０を形成している。尚、図示の例では、前記各部２９ａ、３９、３１ａを繰り返し順番に配置しているが、必ずしもこの様に配置する必要はない。   Then, the first concave portions 29a, 29a and the first convex portions 37, 37 by knurling are alternately formed on the entire bottom of the bottom surface of the locking groove 22b on the thin portion 36. A flat first knurled eye 38 is formed. Furthermore, the first recesses 29a, 29a, the second protrusions 39, 39, and the second recesses 31a, 31a by knurling are only applied to the portion formed in the thick portion 28 in the axial direction of the locking groove 22b. Are arranged in a repeating order over the entire circumference (repeat in the order of the first concave portion 29a → the second convex portion 39 → the second concave portion 31a → the second convex portion 39). Is forming. In the example shown in the drawing, the respective parts 29a, 39, 31a are repeatedly arranged in order, but it is not always necessary to arrange them in this manner.

上述の様に構成する本例の場合、前述した参考例の構造よりも前記第一凹部２９ａ、２９ａの軸方向寸法を大きくしている。この結果、温度上昇の程度が小さい、低温状態での使用時に、前記外輪１５ｃの第一凹部２９ａ、２９ａとプーリ１ｃの内周面に形成された突条３４ａ、３４ａとの係合により、前記外輪１５ｃとこのプーリ１ｃのクリープをより確実に防止できる。その他の部分の構成及び作用は、上述した参考例と同様であるから、同等部分に関する図示並びに説明は省略する。 In the case of this example configured as described above, the axial dimensions of the first recesses 29a and 29a are made larger than the structure of the reference example described above. As a result, at the time of use in a low temperature state where the temperature rise is small, the engagement between the first recesses 29a, 29a of the outer ring 15c and the protrusions 34a, 34a formed on the inner peripheral surface of the pulley 1c, The creep of the outer ring 15c and the pulley 1c can be prevented more reliably. Since the configuration and operation of the other parts are the same as those in the reference example described above, illustration and description regarding the equivalent parts are omitted.

［実施の形態の第２例］
図７は、全ての請求項に対応する、本発明の実施の形態の第２例を示している。本例の場合、転がり軸受１３（図８〜１１参照）を構成する外輪１５ｄの外周面に、図７に梨地で示す様に、ショットブラスト処理或いはバレル加工等によって微細な凹凸（ディンプル）を設けて、前記外周面の表面粗さをＲａ０．１以上としている。そして、プーリと前記外輪１５ｄとを接合する為の接着剤による接合力を向上させている。その他の部分の構成及び作用は、前述した参考例及び上述した実施の形態の第１例と同様であるから、同等部分に関する図示並びに説明は省略する。 [ Second Example of Embodiment]
FIG. 7 shows a second example of an embodiment of the present invention corresponding to all claims. In the case of this example, fine irregularities (dimples) are provided on the outer peripheral surface of the outer ring 15d constituting the rolling bearing 13 (see FIGS. 8 to 11) by shot blasting or barrel processing as shown by a matte surface in FIG. The surface roughness of the outer peripheral surface is Ra 0.1 or more. And the joining force by the adhesive agent for joining a pulley and the said outer ring | wheel 15d is improved. Since the configuration and operation of the other parts are the same as those of the reference example described above and the first example of the embodiment described above, illustration and description regarding equivalent parts are omitted.

１、１ａ〜１ｃ プーリ
２ 張力付与装置
３ ベースプレート
４ 長孔
５ 支持軸
６ 頭部
７ 調整ボルト
８ 折り曲げ板部
９ 通孔
１０ 調整ナット
１１ ロックナット
１２ 支持スリーブ
１３ 転がり軸受
１４ 内輪
１５、１５ａ〜１５ｄ 外輪
１６ 内径側円筒部
１７ 外径側円筒部
１８ 連結部
１９ 補強リブ
２０ 金型
２１ キャビティ
２２、２２ａ 係止溝
２３ 凹部
２４ 凸部
２５、２５ａ ローレット目
２６ 突条
２７、２７ａ 外輪軌道
２８ 肉厚部
２９、２９ａ 第一凹部
３０ 凸部
３１、３１ａ 第二凹部
３２ Ｒ面取り部
３３ Ｒ面取り部
３４ 第一突条
３５ 第二突条
３６ 肉薄部
３７ 第一凸部
３８ 第一ローレット目
３９ 第二凸部
４０ 第二ローレット目 1, 1a to 1c Pulley 2 Tension applying device 3 Base plate 4 Long hole 5 Support shaft 6 Head 7 Adjustment bolt 8 Bending plate portion 9 Through hole 10 Adjustment nut 11 Lock nut 12 Support sleeve 13 Rolling bearing 14 Inner ring 15, 15a-15d Outer ring 16 Inner diameter side cylindrical part 17 Outer diameter side cylindrical part 18 Connection part 19 Reinforcement rib 20 Mold 21 Cavity 22, 22a Locking groove 23 Recessed part 24 Convex part 25, 25a Knurled eye 26 Projection 27, 27a Outer ring raceway 28 Thickness Part 29, 29a First concave part 30 Convex part 31, 31a Second concave part 32 R chamfered part 33 R chamfered part 34 First protrusion 35 Second protrusion 36 Thin part 37 First convex part 38 First knurled eye 39 Second Convex 40 second knurled eye

Claims (2)

外周面にベルトを掛け渡す合成樹脂製のプーリと、このプーリの内径側に保持された転がり軸受とを備え、この転がり軸受は、外周面に単列深溝型の内輪軌道を有する内輪と、内周面に単列深溝型の外輪軌道を有する外輪と、これら内輪軌道と外輪軌道との間に転動自在に設けられた複数個の玉とを備えたものであり、前記外輪を前記プーリの内径側に、モールドした状態で一体的に保持固定しているプーリ装置に於いて、
前記外輪の外周面の軸方向の一部に凹部と凸部とを全周に亙って交互に配置して成る平目のローレット目を形成しており、
このローレット目が、前記外輪の外周面の軸方向の一部に形成された第一ローレット目と、この外輪の外周面のうち、内周面に前記外輪軌道を形成した部分から軸方向に外れた肉厚部に形成された第二ローレット目とから成り、
前記凸部が、前記外輪の外周面の軸方向の一部に形成された第一凸部と、前記肉厚部に形成された第二凸部とから成り、
前記第一ローレット目は、それぞれ複数ずつの第一凹部と前記第一凸部とを、円周方向に関して交互に配置したものであり、前記第二ローレット目は、それぞれ複数の前記第一凹部と前記第二凸部と、これら各第一凹部から円周方向に外れた位置に設けられて、これら各第一凹部よりも大きな深さ寸法を有する、少なくとも１個の第二凹部とを備えたものであり、
前記第一凸部及び前記第二凸部の外径側円周方向両端縁に面取り部を形成した事を特徴とするプーリ装置。 A pulley made of synthetic resin that hangs the belt on the outer peripheral surface, and a rolling bearing held on the inner diameter side of the pulley, the rolling bearing includes an inner ring having a single-row deep groove type inner ring raceway on the outer peripheral surface, An outer ring having a single-row deep groove type outer ring raceway on a peripheral surface, and a plurality of balls provided between the inner ring raceway and the outer ring raceway so as to be freely rollable. the inner diameter side, in the pulley apparatus which holds fixed integrally in a state of mode Rudo,
Forms a flatfish of knurling formed by alternately arranged over the recess and the convex portion in the entire circumference on a part of the axial direction of the outer peripheral surface of the outer ring,
The knurled line is axially disengaged from the first knurled line formed on a part of the outer peripheral surface of the outer ring in the axial direction and the part of the outer peripheral surface of the outer ring where the outer ring raceway is formed on the inner peripheral surface. The second knurled eye formed in the thick part,
The convex portion is composed of a first convex portion formed on a part of the outer peripheral surface of the outer ring in the axial direction and a second convex portion formed on the thick portion,
The first knurls are each formed by alternately arranging a plurality of first recesses and the first projections in the circumferential direction, and the second knurls are each provided with a plurality of the first recesses. Provided with the second convex portion and at least one second concave portion provided at a position deviated in the circumferential direction from each of the first concave portions and having a depth dimension larger than each of the first concave portions. Is,
A pulley apparatus characterized in that chamfered portions are formed at both circumferential edges of the first convex portion and the second convex portion on the outer diameter side. 外輪の外周面のうち、少なくともローレット目が形成された部分に多数の微小凹部を形成した事を特徴とする請求項１に記載したプーリ装置。 2. The pulley apparatus according to claim 1 , wherein a large number of minute recesses are formed at least in a portion of the outer peripheral surface of the outer ring where knurled eyes are formed.
JP2011087210A 2011-04-11 2011-04-11 Pulley device Expired - Fee Related JP5899644B2 (en)

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JP2014149042A (en) * 2013-02-01 2014-08-21 Nihon Isued Corp Synthetic resin pulley
DE102016216940A1 (en) * 2016-09-07 2018-03-08 Aktiebolaget Skf bearing arrangement
DE102019201754A1 (en) * 2019-02-11 2020-08-13 Aktiebolaget Skf Pulley device especially for a tension pulley or a pulley

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JPH11148550A (en) * 1997-11-14 1999-06-02 Ntn Corp Resin pulley
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JP2009041644A (en) * 2007-08-08 2009-02-26 Nsk Ltd Rolling bearing
JP2009174588A (en) * 2008-01-22 2009-08-06 Ntn Corp Bearing with resin pulley
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