TWI620880B - Angular ball bearing - Google Patents
Angular ball bearing Download PDFInfo
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- TWI620880B TWI620880B TW104108845A TW104108845A TWI620880B TW I620880 B TWI620880 B TW I620880B TW 104108845 A TW104108845 A TW 104108845A TW 104108845 A TW104108845 A TW 104108845A TW I620880 B TWI620880 B TW I620880B
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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
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
- F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
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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
- F16C19/163—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 with angular contact
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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
- F16C33/38—Ball cages
- F16C33/41—Ball cages comb-shaped
- F16C33/412—Massive or moulded comb cages, e.g. snap ball cages
- F16C33/414—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages
- F16C33/416—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages made from plastic, e.g. injection moulded comb cages
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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
- F16C33/38—Ball cages
- F16C33/41—Ball cages comb-shaped
- F16C33/418—Details of individual pockets, e.g. shape or ball retaining means
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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
- F16C33/38—Ball cages
- F16C33/44—Selection of substances
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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
- F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
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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
- F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
- F16C2208/20—Thermoplastic resins
- F16C2208/36—Polyarylene ether ketones [PAEK], e.g. PEK, PEEK
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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
- F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
- F16C2208/20—Thermoplastic resins
- F16C2208/40—Imides, e.g. polyimide [PI], polyetherimide [PEI]
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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
- F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
- F16C2208/20—Thermoplastic resins
- F16C2208/60—Polyamides [PA]
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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
- F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
- F16C2208/20—Thermoplastic resins
- F16C2208/66—Acetals, e.g. polyoxymethylene [POM]
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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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/30—Angles, e.g. inclinations
- F16C2240/34—Contact angles
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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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/44—Hole or pocket sizes
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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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/46—Gap sizes or clearances
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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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/70—Diameters; Radii
- F16C2240/80—Pitch circle diameters [PCD]
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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
- F16C2322/00—Apparatus used in shaping articles
- F16C2322/39—General build up of machine tools, e.g. spindles, slides, actuators
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
本發明之保持器(30)係包含大致圓環狀之環部(31)、自環部(31)之正面側或背面側以特定間隔於軸方向突出之複數個柱部(32)、及形成於相鄰之柱部(32)之間之複數個凹穴部(33)之冠型保持器。凹穴部(33)之球面中心位置係較環部(31)之最外徑部(m1)與最內徑部(m2)之徑方向中間位置(M),偏移至徑方向一側。形成凹穴部(33)之柱部(32)之自周方向觀察之側面為將連結環部(31)之徑方向一側面與徑方向另一側面之圓弧(33a)之一部分切除而成者,且包含:第1直線形狀部(33b),其係以切除圓弧(33a)之徑方向一側端部且於軸方向延伸之方式形成。 The retainer (30) of the present invention includes a substantially annular ring portion (31), a plurality of column portions (32) protruding from the front side or the back side of the ring portion (31) in the axial direction at specific intervals, and Crown-shaped retainers of a plurality of recessed portions (33) formed between adjacent pillar portions (32). The spherical center position of the cavity portion (33) is offset from the radial direction intermediate position (M) of the outermost diameter portion (m1) and the innermost diameter portion (m2) of the ring portion (31) to the radial direction side. The side surface of the pillar portion (32) forming the cavity portion (33) viewed from the circumferential direction is obtained by cutting a part of the circular arc (33a) on one side of the radial direction and the other side of the radial direction of the connecting ring portion (31). In addition, the first linear shape portion (33b) is formed by cutting an end portion in the radial direction side of the circular arc (33a) and extending in the axial direction.
Description
本發明係關於斜角滾珠軸承。 The present invention relates to an angular ball bearing.
於NC(Numerical Control:數值控制)車床、銑床、自動換刀數位控制機床(machining center)、複合加工機、五軸加工機等工作機械、或主軸台或安裝加工物之機床之直動輸送機構中,使用將旋轉運動轉換成直線運動之滾珠螺桿。採用斜角滾珠軸承作為旋轉支持該滾珠螺桿軸端之軸承(例如,參照專利文獻1)。該等之軸承係根據使用之工作機械之主軸台或安裝加工物之機床之大小,使用軸承內徑為Φ10mm~Φ100mm左右之尺寸者。 NC (Numerical Control: numerical control) lathes, milling machines, automatic tool-changing digital control machine tools (machining center), composite processing machines, five-axis processing machines and other working machinery, or the spindle table or the machine tool to install the workpiece In the process, a ball screw that converts rotary motion into linear motion is used. An oblique ball bearing is adopted as a bearing that rotatably supports the ball screw shaft end (for example, refer to Patent Document 1). These bearings are based on the size of the spindle table of the working machine or the machine tool on which the workpiece is installed, and the bearing inner diameter is about Φ10mm ~ Φ100mm.
加工中產生之切削載荷、或以高加速使主軸台及機床移動之情形之慣性載荷係經由滾珠螺桿作為軸向載荷負荷於斜角滾珠軸承。最近之工作機械存在基於高效率加工之目的而使切削載荷或快速旋入(fast-forwarding)引起之慣性載荷增大,而對斜角滾珠軸承負荷較大之軸向載荷之傾向。 The cutting load generated during machining, or the inertial load when the spindle table and the machine tool are moved with high acceleration, are loaded to the angular ball bearing as an axial load through a ball screw. Recent work machines tend to increase the inertia load caused by cutting load or fast-forwarding based on the purpose of high-efficiency machining, and tend to increase the axial load on the angular ball bearing.
因此,用於支撐此種滾珠螺桿之斜角滾珠軸承為了增加滾動疲勞壽命,必須使軸方向之負荷容量增加、與用以維持加工精度之高剛性兩者並立。 Therefore, in order to increase the rolling fatigue life of an oblique ball bearing used to support such a ball screw, it is necessary to increase the load capacity in the axial direction and to achieve high rigidity to maintain machining accuracy.
[專利文獻1]日本特開2000-104742號公報 [Patent Document 1] Japanese Patent Laid-Open No. 2000-104742
為使該等兩者並立,雖然只要增大軸承尺寸,使組合之行數變多即可對應,但若增大軸承尺寸,則滾珠螺桿軸端之空間增加,此外,若組合之行數過度地增多,則滾珠螺桿單元部分成寬度較寬之構成。其結果,因工作機械所需估地面積增加或高度方向之尺寸增加,故軸承之大型化或行數增加存在限度。 In order to make these two stand side by side, although the bearing size needs to be increased to increase the number of combined lines, the bearing space of the ball screw shaft increases if the bearing size is increased. In addition, if the number of combined lines is excessive, When the ground is increased, the ball screw unit has a wider width. As a result, there is a limit to the increase in the size of the bearing or the increase in the number of rows due to an increase in the estimated area required for the work machine or an increase in the size in the height direction.
本發明係鑑於上述事情而完成者,其目的在於提供一種於有限之空間中可使軸方向之負荷容量增加與高剛性兩者並立之斜角滾珠軸承。 The present invention has been made in view of the above-mentioned circumstances, and an object thereof is to provide an oblique ball bearing that can increase both the load capacity in the axial direction and high rigidity in a limited space.
本發明之上述目的係藉由下述之構成達成。 The said objective of this invention is achieved by the following structure.
(1) (1)
一種斜角滾珠軸承,其特徵在於包含:外環,其於內周面具有軌道面;內環,其於外周面具有軌道面;複數個滾珠,其等配置於上述外環及上述內環之軌道面之間;及保持器,其係滾珠引導方式者,且係保持上述滾珠使之自由滾動;且上述內環之外周面中,於背面側凹設內環埋頭孔,於正面側凸設內環槽肩部;上述外環之內周面中,於正面側凹設外環埋頭孔,於背面側凸設外環槽肩部;且上述滾珠之接觸角α為45°≦α≦65°;若將上述內環槽肩部之徑方向高度除以上述滾珠直徑所得值設 為Ai,則0.35≦Ai≦0.50;若將上述外環槽肩部之徑方向高度除以上述滾珠直徑所得值設為Ae,則0.35≦Ae≦0.50;上述保持器係冠型保持器,其具有大致圓環狀之環部、自上述環部之正面側或背面側以特定間隔於軸方向突出之複數個柱部、及形成於相鄰之上述柱部之間之複數個凹穴部;上述凹穴部之球面中心位置係較上述環部之最外徑部與最內徑部之徑方向中間位置,偏移至徑方向一側;形成上述凹穴部之上述柱部之自周方向觀察之側面為將連結上述環部之徑方向一側面與徑方向另一側面之圓弧之一部分切除而成者,且包含:第1直線形狀部,其係以切除上述圓弧之徑方向一側端部且於軸方向延伸之方式形成。 An angular ball bearing is characterized by comprising: an outer ring having a track surface on an inner peripheral surface; an inner ring having a track surface on an outer peripheral surface; a plurality of balls arranged on the outer ring and the inner ring Between the track surfaces; and a retainer, which is a ball guide method, and which keeps the balls rolling freely; and in the outer peripheral surface of the inner ring, an inner ring countersink is recessed on the back side and convex on the front side Inner ring groove shoulder; in the inner peripheral surface of the outer ring, an outer ring countersink is recessed on the front side, and an outer ring groove shoulder is protruded on the back side; and the contact angle α of the balls is 45 ° ≦ α ≦ 65 °; If the radial height of the shoulder of the inner ring groove is divided by the ball diameter Is Ai, then 0.35 ≦ Ai ≦ 0.50; if the value obtained by dividing the radial height of the shoulder of the outer ring groove by the ball diameter is set to Ae, 0.35 ≦ Ae ≦ 0.50; the above-mentioned holder is a crown-type holder, which A ring portion having a substantially circular ring shape, a plurality of pillar portions protruding from the front side or the back side of the ring portion at specific intervals in the axial direction, and a plurality of recessed portions formed between the adjacent pillar portions; The spherical center position of the cavity portion is offset from the radial direction intermediate position between the outermost diameter portion and the innermost diameter portion of the ring portion to the radial direction side; the circumferential direction of the column portion forming the cavity portion The side surface to be observed is obtained by cutting out a part of an arc connecting one side of the radial direction of the ring portion and the other side of the radial direction, and includes: a first linear shape portion that cuts the radial direction of the arc The side end portion is formed so as to extend in the axial direction.
(2) (2)
如技術方案(1)之斜角滾珠軸承,其中形成上述凹穴部之上述柱部之自周方向觀察之側面包含:第2直線形狀部,其係將上述圓弧之連結上述第1直線形狀部、與上述環部之上述徑方向一側面之部分切除而形成。 The oblique ball bearing of the technical solution (1), wherein the side surface of the column portion forming the recessed portion viewed from the circumferential direction includes a second linear shape portion that connects the arcs to the first linear shape. The portion and a portion of one side surface in the radial direction of the ring portion are cut out and formed.
(3) (3)
一種斜角滾珠軸承,其特徵在於包含:外環,其於內周面具有軌道面;內環,其於外周面具有軌道面;複數個滾珠,其等配置於上述外環及上述內環之軌道面間;及保持器,其係滾珠引導方式者,且係保持上述滾珠使之自由滾動;且上述內環之外周面中,於背面側凹設內環埋頭孔,於正面側凸設內環槽肩部; 上述外環之內周面中,於正面側凹設外環埋頭孔,於背面側凸設外環槽肩部;且上述滾珠之接觸角α為45°≦α≦65°;若將上述內環槽肩部之徑方向高度除以上述滾珠直徑所得值設為Ai,則0.35≦Ai≦0.50;若將上述外環槽肩部之徑方向高度除以上述滾珠直徑所得值設為Ae,則0.35≦Ae≦0.50;上述保持器係冠型保持器,其具有大致圓環狀之環部、自上述環部之正面側或背面側以特定間隔於軸方向突出之複數個柱部、及形成於相鄰之上述柱部之間之複數個凹穴部;上述凹穴部之球面中心位置係較上述環部之最外徑部與最內徑部之徑方向中間位置,偏移至徑方向一側;形成上述凹穴部之上述柱部之自周方向觀察之側面為將連結上述環部之徑方向一側面與徑方向另一側面之圓弧之一部分切除而成者,且包含:直線形狀部,其係將連結上述圓弧之徑方向一側端部、與上述環部之上述徑方向一側面之部分的至少一部分切除而形成。 An angular ball bearing is characterized by comprising: an outer ring having a track surface on an inner peripheral surface; an inner ring having a track surface on an outer peripheral surface; a plurality of balls arranged on the outer ring and the inner ring; Between the track surfaces; and a retainer, which is a ball-guided method, and which keeps the balls free to roll; and in the outer peripheral surface of the inner ring, an inner ring countersunk hole is recessed on the back side and is convexly set on the front side Ring groove shoulder On the inner peripheral surface of the outer ring, a countersink hole of the outer ring is recessed on the front side, and a shoulder of the outer ring groove is protruded on the back side; and the contact angle α of the balls is 45 ° ≦ α ≦ 65 °; The value obtained by dividing the height of the shoulder in the radial direction by the above-mentioned ball diameter is set to Ai, then 0.35 ≦ Ai ≦ 0.50; if the value obtained by dividing the height in the radial direction of the shoulder of the outer ring by the ball diameter is set to Ae, then 0.35 ≦ Ae ≦ 0.50; the above-mentioned retainer is a crown-type retainer, which has a generally annular ring portion, a plurality of column portions protruding from the front side or the back side of the ring portion at specific intervals in the axial direction, and formed A plurality of recessed portions between the adjacent pillar portions; the spherical center position of the recessed portions is offset from the radial position between the outermost diameter portion and the innermost diameter portion of the ring portion in the radial direction One side; the side surface viewed from the circumferential direction of the column portion forming the cavity portion is a portion obtained by cutting out a part of an arc connecting one side of the ring portion in the radial direction and the other side in the radial direction, and includes: a straight line The shape part connects the end part on one side in the radial direction of the arc, At least a portion of the cut-out portion of a side surface of the above-described radial direction of the ring portion is formed.
(4) (4)
如技術方案(1)至(3)中任一項之斜角滾珠軸承,其中相鄰之上述滾珠彼此之距離L、與圓周率π乘以滾珠節圓直徑dm所得之滾珠節圓周長πdm之關係滿足2.5×10-3≦L/πdm≦13×10-3。 For example, the angular ball bearing of any one of the technical solutions (1) to (3), wherein the distance L between the adjacent balls and the circumference of the ball pitch circle π multiplied by the ball pitch circle diameter dm has a relationship of πdm. Meets 2.5 × 10 -3 ≦ L / πdm ≦ 13 × 10 -3 .
根據本發明之斜角滾珠軸承,因滾珠之接觸角α滿足45°≦α≦65°,故藉由增大接觸角,可增加軸承之軸方向載荷之負荷能力,且可以更大之預壓載荷使用。其結果,可提高軸承進而滾珠螺桿系統之剛性。 According to the angular ball bearing of the present invention, since the contact angle α of the balls satisfies 45 ° ≦ α ≦ 65 °, by increasing the contact angle, the load capacity of the bearing in the axial direction can be increased, and a larger preload can be achieved. Load use. As a result, the rigidity of the bearing and the ball screw system can be improved.
又,將內環槽肩部之徑方向高度除以滾珠直徑所得值設為Ai 時,0.35≦Ai≦0.50,將外環槽肩部之徑方向高度除以滾珠直徑所得值設為Ae時,0.35≦Ae≦0.50,因而可防止軸承之軸方向載荷之負荷能力不足,且使內外環槽肩部之研削加工變得容易。 In addition, the value obtained by dividing the height in the radial direction of the shoulder of the inner ring groove by the ball diameter is set to Ai When the value is 0.35 ≦ Ai ≦ 0.50, and the value obtained by dividing the radial height of the shoulder of the outer ring groove by the ball diameter is set to Ae, 0.35 ≦ Ae ≦ 0.50, which can prevent the bearing's axial load from being insufficient, and Grinding of the inner and outer ring groove shoulders becomes easy.
又,形成凹穴部之柱部之自周方向觀察之側面為將連結環部之徑方向一側面與徑方向另一側面之圓弧之一部分切除而成者,且包含:第1直線形狀部,其係以切除圓弧之徑方向一側端部且於軸方向延伸之方式形成。因此,保持器與滾珠之接觸為線接觸,在保持器於徑方向移動時,滾珠靈活地卡入保持器之凹穴部,從而可抑制保持器朝軸方向之相對移動。藉此,可抑制保持器之徑方向移動量之變化,且可抑制軸承旋轉中振動之增加。又,藉由以線接觸之部分限制保持器,亦可將軸方向之移動抑制成最小限度。其結果,可消除保持器音或保持器提前破損等問題。又,因抑制保持器之凹穴部之節圓位置與滾珠之節圓位置相對於軸方向偏移,故易於進行保持器製造時之外接圓徑或內接圓徑之正確測定。 In addition, the side surface viewed from the circumferential direction of the pillar portion forming the cavity portion is obtained by cutting out a part of a circular arc on one side in the radial direction and the other side in the radial direction of the connecting ring portion, and includes: a first linear shape portion It is formed by cutting the end of one side of the radial direction of the arc and extending in the axial direction. Therefore, the contact between the retainer and the ball is a linear contact. When the retainer moves in the radial direction, the ball flexes into the recessed portion of the retainer, thereby suppressing the relative movement of the retainer in the axial direction. Thereby, a change in the radial movement amount of the cage can be suppressed, and an increase in vibration during the rotation of the bearing can be suppressed. In addition, by restricting the holder with a line-contacting portion, movement in the axial direction can be suppressed to a minimum. As a result, it is possible to eliminate problems such as retainer sounds or premature breakage of the retainer. In addition, since the pitch circle position of the pocket portion of the cage and the pitch circle position of the ball are prevented from being shifted with respect to the axial direction, it is easy to accurately measure the outer circle diameter or the inner circle diameter when the cage is manufactured.
1‧‧‧斜角滾珠軸承 1‧‧‧Angle Ball Bearing
3‧‧‧滾珠 3‧‧‧ball
10‧‧‧外環 10‧‧‧ Outer ring
11‧‧‧軌道面 11‧‧‧ orbital surface
12‧‧‧外環槽肩部 12‧‧‧ Outer ring groove shoulder
13‧‧‧外環埋頭孔 13‧‧‧Outer ring countersunk
14‧‧‧外環倒角 14‧‧‧Chamfer of outer ring
20‧‧‧內環 20‧‧‧ Inner Ring
21‧‧‧軌道面 21‧‧‧ orbital surface
22‧‧‧內環槽肩部 22‧‧‧Inner ring groove shoulder
23‧‧‧內環埋頭孔 23‧‧‧Inner ring countersunk
24‧‧‧內環倒角 24‧‧‧Inner ring chamfer
30‧‧‧保持器 30‧‧‧ retainer
31‧‧‧環部 31‧‧‧Ring
31a‧‧‧環部之徑方向內側面 31a‧‧‧Inner side of diameter of ring
31b‧‧‧環部之徑方向外側面 31b‧‧‧outer side of the ring
32‧‧‧柱部 32‧‧‧ pillar
33‧‧‧凹穴部 33‧‧‧Concave
33a‧‧‧圓弧 33a‧‧‧arc
33b‧‧‧第1直線形狀部 33b‧‧‧The first linear shape part
33c‧‧‧第2直線形狀部 33c‧‧‧The second linear shape part
33d‧‧‧凹穴部之徑方向內側端部 33d‧‧‧Inner end in the radial direction of the cavity
33e‧‧‧圓之徑方向內側端部 33e‧‧‧Circular diameter direction inside end
33f‧‧‧圓之徑方向外側端部 33f‧‧‧outer end
33g‧‧‧第3直線形狀部 33g‧‧‧The third linear shape part
34‧‧‧缺口部 34‧‧‧Gap
35‧‧‧角部 35‧‧‧ Corner
100‧‧‧深槽軸承 100‧‧‧Deep Groove Bearing
110‧‧‧外環 110‧‧‧outer ring
120‧‧‧內環 120‧‧‧ Inner Ring
130‧‧‧保持器 130‧‧‧ retainer
A‧‧‧箭頭 A‧‧‧arrow
A‧‧‧中心點 A‧‧‧center
A-A'‧‧‧剖面 A-A'‧‧‧ section
B‧‧‧中心點 B‧‧‧ Center
C‧‧‧交點 C‧‧‧ intersection
D‧‧‧交點 D‧‧‧ intersection
D1‧‧‧外徑 D1‧‧‧ Outside diameter
D2‧‧‧外徑 D2‧‧‧ Outside diameter
D3‧‧‧內徑 D3‧‧‧Inner diameter
D4‧‧‧內徑 D4‧‧‧Inner diameter
Dw‧‧‧滾珠直徑 Dw‧‧‧ball diameter
dm‧‧‧滾珠節圓直徑 dm‧‧‧ball pitch circle diameter
E‧‧‧中點 E‧‧‧ Midpoint
F‧‧‧徑方向載荷 F‧‧‧ Radial load
He‧‧‧外環槽肩部之徑方向高度 He‧‧‧ Radial height of outer shoulder
Hi‧‧‧內環槽肩部之徑方向高度 Hi‧‧‧Inner ring groove shoulder height in radial direction
L‧‧‧滾珠間距離 L‧‧‧ Distance between balls
M‧‧‧徑方向中間位置 M‧‧‧ center position in radial direction
m1‧‧‧最外徑部 m1‧‧‧most outer diameter part
m2‧‧‧最內徑部 m2‧‧‧ innermost diameter
O‧‧‧節圓中心 O‧‧‧ Festival Circle Center
Oi‧‧‧滾珠中心 Oi‧‧‧Ball Center
P‧‧‧圓中心 P‧‧‧Circle Center
r‧‧‧半徑 r‧‧‧ radius
r1‧‧‧半徑 r1‧‧‧ radius
T‧‧‧滾珠中心間距離 T‧‧‧Ball center distance
VI-VI‧‧‧線 VI-VI‧‧‧line
VII-VII‧‧‧線 Line VII-VII‧‧‧
X‧‧‧起點 X‧‧‧ starting point
XIII-XIII‧‧‧線 XIII-XIII‧‧‧line
XIV-XIV‧‧‧線 XIV-XIV‧‧‧line
XIX-XIX‧‧‧線 XIX-XIX‧‧‧line
XV‧‧‧方向 XV‧‧‧ direction
XXIII‧‧‧方向 XXIII‧‧‧ direction
α‧‧‧接觸角 α‧‧‧ contact angle
θ‧‧‧角度 θ‧‧‧ angle
△A‧‧‧軸方向移動量 △ A‧‧‧Axis movement
△R‧‧‧徑方向移動量 △ R‧‧‧ Radial movement
△Re‧‧‧徑方向間隙 △ Re‧‧‧Radial clearance
△Ri‧‧‧徑方向間隙 △ Ri‧‧‧Radial clearance
△S1‧‧‧軸方向距離 △ S1‧‧‧Axis distance
△S2‧‧‧軸方向距離 △ S2‧‧‧Axis distance
圖1係本發明之實施形態之斜角滾珠軸承之剖面圖。 FIG. 1 is a sectional view of an angular ball bearing according to an embodiment of the present invention.
圖2係並列組合圖1之斜角滾珠軸承之剖面圖。 FIG. 2 is a sectional view of the angular ball bearing of FIG. 1 combined side by side.
圖3係保持器之側面圖。 Figure 3 is a side view of the holder.
圖4係自軸方向一側觀察保持器之圖。 Fig. 4 is a view of the retainer viewed from one side in the axial direction.
圖5係自軸方向另一側觀察保持器之圖。 Fig. 5 is a view of the retainer viewed from the other side in the axial direction.
圖6係圖4之VI-VI剖面向視圖。 FIG. 6 is a sectional view taken along the line VI-VI in FIG. 4.
圖7係圖4之VII-VII剖面向視圖。 FIG. 7 is a sectional view taken along the line VII-VII in FIG. 4.
圖8係先前之深槽滾珠軸承之剖面圖。 Figure 8 is a sectional view of a previous deep groove ball bearing.
圖9係自軸方向一側觀察負荷徑方向載荷時之保持器之圖。 Fig. 9 is a view of a retainer when a load is viewed in a radial direction from a side in the axial direction.
圖10係對保持器負荷徑方向載荷時之斜角滾珠軸承之剖面圖。 Fig. 10 is a cross-sectional view of an angular ball bearing when a radial load is applied to a cage load.
圖11係用以說明複數個滾珠之配置狀態之圖。 FIG. 11 is a diagram for explaining an arrangement state of a plurality of balls.
圖12係先前之斜角滾珠軸承之剖面圖。 Figure 12 is a sectional view of a conventional angular ball bearing.
圖13係圖12之保持器及滾珠之XIII-XIII剖面圖。 FIG. 13 is a sectional view taken along the line XIII-XIII of the retainer and the ball of FIG. 12.
圖14係於圖12之保持器及滾珠中,以一點鏈線之方式顯示保持器之凹穴部於軸方向移動時之XIV-XIV剖面圖。 FIG. 14 is a cross-sectional view of the XIV-XIV when the pocket portion of the holder is moved in the axial direction by a one-point chain line in the holder and the ball of FIG. 12.
圖15係於圖12自XV方向觀察保持器之圖。 Fig. 15 is a view of the holder viewed from the XV direction in Fig. 12.
圖16係顯示本發明之保持器之圖。 Fig. 16 is a diagram showing a holder of the present invention.
圖17係變化例之斜角滾珠軸承之剖面圖。 Fig. 17 is a sectional view of a beveled ball bearing according to a modification.
圖18係自軸方向一側觀察變化例之保持器之圖。 Fig. 18 is a view of a retainer according to a modification as viewed from one side in the axial direction.
圖19係圖18之XIX-XIX剖面向視圖。 FIG. 19 is a sectional view taken along the line XIX-XIX in FIG. 18.
圖20係本發明之實施形態之斜角滾珠軸承之剖面圖。 Fig. 20 is a sectional view of an angular ball bearing according to an embodiment of the present invention.
圖21係並列組合圖20之斜角滾珠軸承之剖面圖。 Fig. 21 is a sectional view of the angular ball bearing of Fig. 20 combined in parallel.
圖22係對保持器負荷徑方向載荷時之斜角滾珠軸承之剖面圖。 Fig. 22 is a sectional view of an angular ball bearing when a radial load is applied to a retainer load.
圖23(a)係保持器之側面圖,(b)係(a)之A-A'剖面之XXIII方向向視圖。 Fig. 23 (a) is a side view of the holder, and (b) is a view taken along the line XXIII of the AA 'section of (a).
圖24係變化例之斜角滾珠軸承之剖面圖。 Fig. 24 is a sectional view of a beveled ball bearing according to a modification.
以下,對本發明之各實施形態之斜角滾珠軸承,使用圖式進行說明。 Hereinafter, the angular ball bearing according to each embodiment of the present invention will be described using drawings.
如圖1所示,本實施形態之斜角滾珠軸承1包含:外環10,其於內周面具有軌道面11;內環20,其於外周面具有軌道面21;複數個滾珠3,其等配置於外環10及內環20之軌道面11、21間;及保持器30,其係滾珠引導方式者,且係保持滾珠3使之自由滾動。 As shown in FIG. 1, the angular ball bearing 1 of this embodiment includes an outer ring 10 having a track surface 11 on an inner peripheral surface, an inner ring 20 having a track surface 21 on an outer peripheral surface, and a plurality of balls 3 which It is arranged between the orbital surfaces 11 and 21 of the outer ring 10 and the inner ring 20; and the retainer 30, which is a ball guide method, and the ball 3 is kept to roll freely.
外環10之內周面係具有:外環槽肩部12,其較軌道面11凸設於更靠向背面側(負荷側,圖1中左側);及外環埋頭孔13,其較軌道面11凹設於更靠向正面側(反負荷側,圖1中右側)。 The inner peripheral surface of the outer ring 10 includes: an outer ring groove shoulder portion 12 which is convexly arranged on the back side (load side, left side in FIG. 1) than the track surface 11; and an outer ring countersunk hole 13 which is more than a rail The surface 11 is recessed further toward the front side (anti-load side, right side in FIG. 1).
內環20之外周面係具有:內環槽肩部22,其較軌道面21凸設於更靠向正面側(負荷側,圖1中右側);及內環埋頭孔23,其較軌道面21凹設於更靠向背面側(相反負荷側,圖1中左側)。 The outer peripheral surface of the inner ring 20 has: an inner ring groove shoulder portion 22 which is convexly arranged on the front side (load side, right side in FIG. 1) than the track surface 21; and an inner ring countersink 23 which is more than the track surface 21 is recessed toward the back side (opposite load side, left side in FIG. 1).
此處,若將內環埋頭孔23之外徑設為D1,將內環槽肩部22之外徑設為D2,則設為D1<D2,且,若將外環埋頭孔13之內徑設為D3,將外環槽肩部12之內徑設為D4,則設為D3>D4。如此,因增大內環槽肩部22之外徑D2,且縮小外環槽肩部12之內徑D4,故可將滾珠3之接觸角α設定得較大。更具體而言,藉由以上述方式設定外徑D2及內徑D4,可將接觸角α設為45°≦α≦65°左右,且即便考慮軸承製作時之接觸角α之變動,亦可設為50°≦α≦60°左右,並可增大接觸角α。 Here, if the outer diameter of the inner ring countersink 23 is D1 and the outer diameter of the inner ring groove shoulder 22 is D2, then D1 <D2, and if the inner diameter of the outer ring countersink 13 is set Let D3, and if the inner diameter of the outer ring groove shoulder 12 is D4, then D3> D4. In this way, since the outer diameter D2 of the inner ring groove shoulder portion 22 is increased and the inner diameter D4 of the outer ring groove shoulder portion 12 is reduced, the contact angle α of the ball 3 can be set to be large. More specifically, by setting the outer diameter D2 and the inner diameter D4 as described above, the contact angle α can be set to about 45 ° ≦ α ≦ 65 °, and even if the variation of the contact angle α at the time of bearing production is considered, It is set to about 50 ° ≦ α ≦ 60 °, and the contact angle α can be increased.
又,若將內環槽肩部22之徑方向高度Hi除以滾珠3之直徑Dw所得值設為Ai(Ai=Hi/Dw),則以滿足0.35≦Ai≦0.50之方式設定,且若將外環槽肩部12之徑方向高度He除以滾珠3之直徑Dw所得值設為Ae(Ae=He/Dw),則以滿足0.35≦Ae≦0.50之方式設定。 In addition, if the value obtained by dividing the height Hi in the radial direction of the shoulder 22 of the inner ring groove by the diameter Dw of the ball 3 is set to Ai (Ai = Hi / Dw), then 0.35 ≦ Ai ≦ 0.50 is set, and if The value obtained by dividing the height He of the shoulder 12 of the outer ring in the radial direction by the diameter Dw of the ball 3 is set to Ae (Ae = He / Dw), and it is set to satisfy 0.35 ≦ Ae ≦ 0.50.
在假設0.35>Ai或0.35>Ae之情形時,因內環槽肩部22或外環槽肩部12之徑方向高度Hi、He相對於滾珠3之直徑Dw過小,故接觸角α未滿45°,軸承之軸方向載荷之負荷能力不足。又,於0.50<Ai或0.50<Ae之情形時,因外環10及內環20之軌道面11、21形成為超出滾珠3之節圓直徑dm,故外環槽肩部12及內環槽肩部22之研磨加工較困難,而不被期望。 In the case of 0.35> Ai or 0.35> Ae, the contact angle α is less than 45 because the radial heights Hi and He of the inner ring groove shoulder 22 or the outer ring groove shoulder 12 are too small relative to the diameter Dw of the ball 3. °, the load capacity of the bearing in the axial direction is insufficient. In the case of 0.50 <Ai or 0.50 <Ae, since the track surfaces 11 and 21 of the outer ring 10 and the inner ring 20 are formed to exceed the pitch circle diameter dm of the ball 3, the outer ring groove shoulder 12 and the inner ring groove The grinding of the shoulder 22 is difficult and undesirable.
又,於外環槽肩部12之背面側端部,設置有隨著朝向背面側而朝向徑方向外側之錐形狀之外環倒角14,且於內環槽肩部22之正面側端部,設置有隨著朝向正面側而朝向徑方向內側之錐形狀之內環倒角24。該等外環倒角14及內環倒角24之徑方向寬度大於外環槽肩部12及內環槽肩部22之徑方向高度He、Hi之一半,且設定為較大之值。 A tapered outer ring chamfer 14 is formed on the back side end portion of the outer ring groove shoulder portion 12 toward the outer side in the radial direction as it faces the back side, and the front side end portion of the inner ring groove shoulder portion 22 is provided. A tapered inner ring chamfer 24 is provided toward the inside in the radial direction as it faces the front side. The radial widths of the outer ring chamfers 14 and the inner ring chamfers 24 are larger than one and a half of the radial heights He and Hi of the outer ring groove shoulders 12 and the inner ring groove shoulders 22, and are set to larger values.
此種斜角滾珠軸承1係如圖2所示,可並列組合使用。由於本實 施形態之斜角滾珠軸承1係將外環槽肩部12及內環槽肩部22設置至滾珠3之節圓直徑dm之附近,故,假設未設置外環倒角14及內環倒角24,則一斜角滾珠軸承1之內環20與另一斜角滾珠軸承1之外環10彼此干涉,導致軸承旋轉中發生不佳狀況。又,以油潤滑使用之情形時,假設未設置外環倒角14及內環倒角24,則油未通過各斜角滾珠軸承1之間,而油之流通變差、潤滑不良、或油大量殘留於軸承內部而引起溫度上升。如此,藉由設置外環倒角14及內環倒角24,可實現防止內環20及外環10彼此之干涉,及提高油之流通性。另,外環倒角14及內環倒角24係未必設置兩者,只要設置至少一者即可。 This type of angular ball bearing 1 is shown in Fig. 2 and can be used in combination. Since the real The oblique angle ball bearing 1 in the configuration is provided with the outer ring groove shoulder portion 12 and the inner ring groove shoulder portion 22 near the pitch circle diameter dm of the ball 3. Therefore, it is assumed that the outer ring chamfer 14 and the inner ring chamfer are not provided. 24, the inner ring 20 of one oblique ball bearing 1 and the outer ring 10 of the other oblique ball bearing 1 interfere with each other, resulting in a poor condition in the rotation of the bearing. In the case of oil lubrication, it is assumed that the outer ring chamfer 14 and the inner ring chamfer 24 are not provided, and the oil does not pass between the angled ball bearings 1 and the oil flow becomes poor, the lubrication is poor, or the oil is not provided. A large amount remains in the bearing and causes a temperature rise. In this way, by providing the outer ring chamfer 14 and the inner ring chamfer 24, it is possible to prevent the inner ring 20 and the outer ring 10 from interfering with each other, and improve the oil flowability. In addition, the outer ring chamfer 14 and the inner ring chamfer 24 are not necessarily both provided, as long as at least one is provided.
接著,參照圖3~7,對保持器30之構成進行詳細說明。保持器30係包含合成樹脂之滾珠引導方式之塑膠保持器,構成該保持器30之基礎樹脂係聚醯胺樹脂。另,聚醯胺樹脂之種類並未受限制者,除聚醯胺以外,亦可為聚縮醛樹脂、聚醚醚酮、聚醯亞胺等其他合成樹脂。進而,於基礎樹脂中,添加玻璃纖維、碳纖維、芳香族聚醯胺纖維等作為強化材料。又,保持器30係藉由射出成形或切削加工而製造。 Next, the configuration of the holder 30 will be described in detail with reference to FIGS. 3 to 7. The retainer 30 is a ball-guided plastic retainer including a synthetic resin, and the base resin of the retainer 30 is a polyamide resin. In addition, the type of the polyamide resin is not limited, and in addition to the polyamide, other synthetic resins such as polyacetal resin, polyetheretherketone, and polyimide may also be used. Further, as the reinforcing material, glass fibers, carbon fibers, aromatic polyamide fibers, and the like are added to the base resin. The retainer 30 is manufactured by injection molding or cutting.
保持器30為冠型保持器,其具有:與內環20及外環10同軸而配置之大致圓環狀之環部31(參照圖1)、自環部31之背面側以特定之間隔於軸方向突出之複數個柱部32、及形成於相鄰之柱部32之間之複數個凹穴部33。 The retainer 30 is a crown-shaped retainer, and has a substantially annular ring portion 31 (refer to FIG. 1) arranged coaxially with the inner ring 20 and the outer ring 10. A plurality of pillar portions 32 protruding in the axial direction, and a plurality of recessed portions 33 formed between adjacent pillar portions 32.
此處,於本實施形態之斜角滾珠軸承1中,為實現軸方向載荷之高負荷能力,而增大外環槽肩部12及內環槽肩部22之徑方向高度He、Hi,因而軸承內部空間減少。因此,在配置於此種軸承內部空間之保持器30為冠型保持器(單側環構造)之情形時,採用於外環埋頭孔13與內環槽肩部22之間配置環部31,且於外環10及內環20之軌道面11、21之間配置柱部32、並於柱部32之徑方向外側端部連接環部31之構造。 Here, in the angular ball bearing 1 of this embodiment, in order to achieve a high load capacity in the axial direction, the radial heights He and Hi of the outer ring groove shoulder portion 12 and the inner ring groove shoulder portion 22 are increased. Reduced bearing internal space. Therefore, when the retainer 30 disposed in the bearing internal space is a crown-type retainer (single-side ring structure), the ring portion 31 is arranged between the outer ring countersunk hole 13 and the inner ring groove shoulder portion 22, A structure in which a pillar portion 32 is arranged between the track surfaces 11 and 21 of the outer ring 10 and the inner ring 20 and is connected to the ring portion 31 at the radially outer end of the pillar portion 32.
即,如圖7所示,設為凹穴部33之球面中心位置較環部31之最外徑部m1與最內徑部m2之徑方向中間位置M,偏移至徑方向內側(徑方向一側)之構造。此處,凹穴部33之球面中心位置係與滾珠3之中心Oi一致之位置。又,環部31之最外徑部m1係徑方向外側面31b,最內徑部m2係徑方向內側面31a。另,於圖示之例中,凹穴部33之球面中心位置較環部31之最內徑部m2偏移至徑方向內側。 That is, as shown in FIG. 7, it is assumed that the spherical center position of the recessed portion 33 is shifted to the inner side in the radial direction (radial direction) from the radial direction intermediate position M between the outermost diameter portion m1 and the innermost diameter portion m2 of the ring portion 31. Side). Here, the spherical center position of the pocket portion 33 is a position that coincides with the center Oi of the ball 3. The outermost diameter portion m1 of the ring portion 31 is an outer surface 31b in the radial direction, and the innermost diameter portion m2 is an inner surface 31a in the radial direction. In the example shown in the figure, the spherical center position of the recessed portion 33 is shifted to the inner side in the radial direction from the innermost diameter portion m2 of the ring portion 31.
如圖7所示,形成凹穴部33之柱部32之自周方向觀察之側面為將連結環部31之徑方向內側面(徑方向一側面)31a與徑方向外側面(徑方向另一側面)31b之圓弧33a之一部分切除而成者。圓弧33a之中心係以P表示,半徑係以r表示。 As shown in FIG. 7, the side surface of the pillar portion 32 forming the cavity portion 33 as viewed from the circumferential direction is the inner side surface (one side in the radial direction) 31 a of the radial direction and the outer side surface (the other side in the radial direction) connecting the ring portion 31. A part of the arc 33a of the side surface 31b is cut out. The center of the arc 33a is represented by P, and the radius is represented by r.
更具體而言,柱部32之自周方向觀察之側面包含:第1直線形狀部33b,其係以切除圓弧33a之徑方向內側端部(徑方向一側端部)且於軸方向延伸之方式形成。第1直線形狀部33b係配置於較圓弧33a之中心P更靠向背面側。又,第1直線形狀部33b係與滾珠3之中心Oi(凹穴部33之球面中心)於軸方向重疊。 More specifically, the side surface of the pillar portion 32 viewed from the circumferential direction includes a first linear shape portion 33b which is a radial-direction inner end portion (radial-direction-side end portion) cut away from the arc 33a and extends in the axial direction. Way of forming. The first linear shape portion 33b is disposed closer to the back side than the center P of the arc 33a. The first linear shape portion 33b overlaps the center Oi of the ball 3 (the spherical surface center of the cavity portion 33) in the axial direction.
再者,柱部32之自周方向觀察之側面包含:第2直線形狀部33c,其係將圓弧33a之連結第1直線形狀部33b之正面側之端部、與環部31之徑方向內側面31a之背面側之端部之部分切除而形成。因此,第2直線形狀部33c係設為隨著朝向正面側(環部31側)而朝向徑方向外側之直線形狀。 In addition, the side surface of the pillar portion 32 viewed from the circumferential direction includes a second linear shape portion 33c, which is an end portion on the front side that connects the arc 33a to the first linear shape portion 33b, and the radial direction of the ring portion 31. A part of the end portion on the back side of the inner surface 31a is cut out and formed. Therefore, the second linear shape portion 33c has a linear shape that faces outward in the radial direction as it goes toward the front side (the ring portion 31 side).
又,柱部32之自周方向觀察之側面包含:第3直線形狀部33g,其係以切除圓弧33a之徑方向外側端部(徑方向另一側端部)且於軸方向延伸之方式形成。第3直線形狀部33g與環部31之徑方向外側面31b形成於相同平面上,且與該徑方向外側面31b無階差連接。 In addition, the side surface of the pillar portion 32 viewed from the circumferential direction includes a third linear shape portion 33g which is formed by cutting out the radial end portion (the other end portion in the radial direction) of the radial direction of the arc 33a and extending in the axial direction. form. The third linear shape portion 33g is formed on the same plane as the radial outer surface 31b of the ring portion 31, and is connected to the radial outer surface 31b without a step.
如此,柱部32之自周方向觀察之側面成為連接有第3直線形狀部33g、圓弧33a、第1直線形狀部33b、及第2直線形狀部33c之形狀。 In this way, the side surface of the pillar portion 32 viewed from the circumferential direction has a shape in which the third linear shape portion 33g, the arc 33a, the first linear shape portion 33b, and the second linear shape portion 33c are connected.
又,如圖6所示,形成凹穴部33之柱部32之周方向兩側面、及環部31之背面側(柱部32側)之側面係形成為自徑方向觀察時與滾珠3相似形狀之球面狀。此處,柱部32之頂端係於周方向中間設置有缺口部34,且分叉。藉此,以射出成型製造保持器30時,可防止因強制拔出形成凹穴部33之模具構件而引起之柱部32之凹穴部33側之角部35之破損。 As shown in FIG. 6, both sides in the circumferential direction of the pillar portion 32 forming the cavity portion 33 and the side surfaces on the back side (pillar portion 32 side) of the ring portion 31 are formed similar to the ball 3 when viewed from the radial direction. Spherical shape. Here, the top end of the pillar portion 32 is provided with a notch portion 34 at the middle in the circumferential direction and is branched. Accordingly, when the retainer 30 is manufactured by injection molding, the corner portion 35 on the side of the recessed portion 33 of the pillar portion 32 caused by forcibly pulling out the mold member forming the recessed portion 33 can be prevented.
又,添加至保持器30材料之合成樹脂之強化材料之比例較佳為5~30重量%。假設,合成樹脂成分中強化材料之比例超過30重量%,則因保持器30之柔軟性降低,故在保持器30成形時自凹穴部33強制拔出模具時、或組裝軸承時將滾珠3壓入凹穴部33時,導致柱部32之角部35破損。又,保持器30之熱膨脹係依存於基礎材料即樹脂材料之線膨脹係數,因而,若強化材料之比例少於5重量%,則軸承旋轉中之保持器30之熱膨脹相對於滾珠3之節圓直徑dm之膨脹變得更大,導致滾珠3與保持器30之凹穴部33相抵觸,引起燒焦等不佳狀況。因此,藉由將合成樹脂成分中之強化材料之比例設在5~30重量%之範圍內,可防止上述不佳狀況。 The proportion of the reinforcing material of the synthetic resin added to the material of the holder 30 is preferably 5 to 30% by weight. Assuming that the proportion of the reinforcing material in the synthetic resin component exceeds 30% by weight, the flexibility of the retainer 30 is reduced. Therefore, when the retainer 30 is formed, the ball 3 is forcibly pulled out of the mold from the cavity 33 or the bearing is assembled. When the recessed portion 33 is pushed in, the corner portion 35 of the pillar portion 32 is damaged. In addition, the thermal expansion of the retainer 30 depends on the linear expansion coefficient of the base material, that is, the resin material. Therefore, if the proportion of the reinforcing material is less than 5% by weight, the thermal expansion of the retainer 30 during bearing rotation relative to the pitch of the ball 3 The expansion of the diameter dm becomes larger, causing the ball 3 to collide with the recessed portion 33 of the retainer 30, causing an unfavorable condition such as burning. Therefore, by setting the proportion of the reinforcing material in the synthetic resin component within the range of 5 to 30% by weight, it is possible to prevent the above-mentioned bad situation.
另,作為保持器30之合成樹脂材料,應用聚醯胺、聚醚醚酮、聚苯硫醚、聚醯亞胺等之樹脂,且作為強化材料,應用玻璃纖維、碳纖維、芳香族聚醯胺纖維等。 In addition, as the synthetic resin material of the holder 30, resins such as polyamine, polyetheretherketone, polyphenylene sulfide, polyimide, and the like, and glass fiber, carbon fiber, and aromatic polyamidine are used as the reinforcing material. Fiber, etc.
此處,如圖8所示,具有先前之冠形保持器之深槽滾珠軸承100係保持器130與內環120或外環110於徑方向未重疊。因此,即使因深槽滾珠軸承100之旋轉始動時或停止時之慣性,使保持器130超過設計值,而對於內環120或外環110相對於軸方向移動,保持器130與內環120或外環110亦未彼此干涉。 Here, as shown in FIG. 8, the deep groove ball bearing 100 having the previous crown-shaped cage 100 is a cage 130 and the inner ring 120 or the outer ring 110 does not overlap in the radial direction. Therefore, even if the retainer 130 exceeds the design value due to the inertia at the start or stop of the rotation of the deep groove ball bearing 100, the retainer 130 and the inner ring 120 or the inner ring 120 or the outer ring 110 move relative to the axial direction. The outer rings 110 also do not interfere with each other.
然而,如本實施形態之斜角滾珠軸承1,在保持器30與內環20或外環10於徑方向重疊之情形時,保持器30超過設計值,且對於內環20 或外環10相對性於軸方向移動時,存在保持器30與內環20或外環10彼此干涉之可能性。假設,柱部32之自周方向觀察之側面為不具有第2直線形狀部33c(參照圖7)形狀之情形時,保持器30與內環20之間之軸方向距離△S1(參照圖1)變窄、且保持器30與內環20彼此干涉之可能性變高。若保持器30與內環20彼此干涉,則於保持器30與內環20干涉時轉矩變動,無法作為滾珠螺桿系統正確定位,且因干涉時之摩擦而磨損保持器30,導致保持器30之破損。此外,保持器30磨損時產生之磨損粉末成為異物,會造成軸承之潤滑狀態變差,其結果從而縮短軸承之壽命。 However, as in the angular ball bearing 1 of this embodiment, when the retainer 30 overlaps with the inner ring 20 or the outer ring 10 in the radial direction, the retainer 30 exceeds the design value, and the inner ring 20 Or when the outer ring 10 moves relative to the axial direction, there is a possibility that the retainer 30 and the inner ring 20 or the outer ring 10 interfere with each other. It is assumed that the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 when the side surface of the pillar portion 32 viewed from the circumferential direction is not in the shape of the second linear shape portion 33c (see FIG. 7) (see FIG. 1) ) Becomes narrower, and the possibility that the retainer 30 and the inner ring 20 interfere with each other becomes high. If the retainer 30 and the inner ring 20 interfere with each other, the torque changes when the retainer 30 and the inner ring 20 interfere, and cannot be positioned correctly as a ball screw system, and the retainer 30 is worn due to friction during the interference, resulting in the retainer 30 Broken. In addition, the abrasion powder generated when the retainer 30 is worn becomes a foreign substance, which causes the lubrication state of the bearing to deteriorate, and as a result, the life of the bearing is shortened.
因此,如本實施形態之斜角滾珠軸承1,藉由柱部32之自周方向觀察之側面具有第2直線形狀部33c,可進一步擴大保持器30與內環20之間之軸方向距離△S1,且可降低保持器30與內環20彼此干涉之可能性。 Therefore, like the angular ball bearing 1 of this embodiment, the second linear shape portion 33c is provided on the side surface of the column portion 32 when viewed from the circumferential direction, and the axial distance Δ between the retainer 30 and the inner ring 20 can be further increased. S1, and the possibility that the retainer 30 and the inner ring 20 interfere with each other can be reduced.
又,如本實施形態之斜角滾珠軸承1,為維持較大之接觸角α,而分別將外環槽肩部12及內環槽肩部22之徑方向高度He、Hi提高至滾珠3之節圓直徑dm附近之情形時,外環10及內環20間之徑方向空間變窄,且位於外環10及內環20間之空間之保持器30之環部31之徑方向壁厚無法相對於標準軸承加厚。尤其,於冠形保持器之情形時,由於環部31僅存在於保持器30之軸方向一側,故有壁厚不足引起環部31之強度降低之虞。 In addition, like the angular ball bearing 1 of this embodiment, in order to maintain a large contact angle α, the radial heights He and Hi of the outer ring groove shoulder portion 12 and the inner ring groove shoulder portion 22 are increased to those of the ball 3, respectively. When the pitch circle diameter is near dm, the radial direction space between the outer ring 10 and the inner ring 20 becomes narrow, and the radial thickness of the ring portion 31 of the retainer 30 located in the space between the outer ring 10 and the inner ring 20 cannot be achieved. Thicker than standard bearings. In particular, in the case of a crown-shaped retainer, since the ring portion 31 exists only on one side in the axial direction of the retainer 30, the wall thickness may be insufficient to cause the strength of the ring portion 31 to decrease.
再者,保持器30之材料為聚醯胺樹脂、聚縮醛樹脂、聚醚醚酮、聚醯亞胺等合成樹脂,對基礎樹脂之強化纖維含有率亦設為30重量%以下。因此,保持器30之環部31之強度往往較低,在徑方向之衝擊載荷或振動載荷增加時,保持器30於徑方向彎曲。另,於圖9中以虛線,於圖10中以一點鏈線示意性表示對保持器30負荷徑方向載荷F,且於徑方向彎曲之情形之形狀之一例。因保持器30於徑方向彎 曲,導致保持器30之徑方向位置接近內環20側或外環10側。因此,保持器30與內環20之間之軸方向距離△S1變窄,且保持器30與內環20彼此干涉之可能性變高。在假設柱部32之自周方向觀察之側面為不具有第2直線形狀部33c之形狀之情形時,保持器30與內環20之間之軸方向距離△S1變窄,且保持器30與內環20彼此干涉之可能性變高。因此,如本實施形態之斜角滾珠軸承1,藉由柱部32之自周方向觀察之側面具有第2直線形狀部33c,可進一步擴大保持器30與內環20之間之軸方向距離△S1,且可降低保持器30與內環20彼此干涉之可能性。 In addition, the material of the holder 30 is synthetic resin such as polyamide resin, polyacetal resin, polyetheretherketone, and polyimide, and the content of reinforcing fibers in the base resin is also set to 30% by weight or less. Therefore, the strength of the ring portion 31 of the retainer 30 tends to be low, and when the impact load or vibration load in the radial direction increases, the retainer 30 bends in the radial direction. An example of a shape in which the radial load F is applied to the retainer 30 and the radial load F is shown by a dotted line in FIG. 9 and a one-dot chain line in FIG. 10 is shown. Because the retainer 30 bends in the radial direction This causes the radial position of the retainer 30 to be closer to the inner ring 20 side or the outer ring 10 side. Therefore, the axial distance ΔS1 between the retainer 30 and the inner ring 20 becomes narrow, and the possibility that the retainer 30 and the inner ring 20 interfere with each other becomes high. When it is assumed that the side surface of the pillar portion 32 viewed from the circumferential direction is not the shape of the second linear shape portion 33c, the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 becomes narrow, and the retainer 30 and The possibility that the inner rings 20 interfere with each other becomes high. Therefore, like the angular ball bearing 1 of this embodiment, the second linear shape portion 33c is provided on the side surface of the column portion 32 when viewed from the circumferential direction, and the axial distance Δ between the retainer 30 and the inner ring 20 can be further increased. S1, and the possibility that the retainer 30 and the inner ring 20 interfere with each other can be reduced.
又,因位於外環10及內環20間之空間之保持器30之環部31之徑方向壁厚無法相對於標準軸承加厚,故存在環部31之彎曲剛性不足之情形。於該情形時,如圖6之箭頭A所示,因軸承使用時作用於保持器30之柱部32之離心力,而導致柱部32之前端朝徑方向外側擴徑,且角部35易於於周方向擴大。因此,保持器30之軸方向移動量△A變大。如此於保持器30之軸方向移動量△A變大之情形時,保持器30與內環20間之軸方向距離△S1變窄,且保持器30與內環20彼此干涉之可能性變高。在假設柱部32之自周方向觀察之側面為不具有第2直線形狀部33c之形狀之情形時,保持器30與內環20之間之軸方向距離△S1變窄,且保持器30與內環20彼此干涉之可能性變高。因此,如本實施形態之斜角滾珠軸承1,藉由於柱部32之自周方向觀察之側面形成第2直線形狀部33c,可進一步擴大保持器30與內環20之間之軸方向距離△S1,且可降低保持器30與內環20彼此干涉之可能性。 In addition, since the wall thickness in the radial direction of the ring portion 31 of the retainer 30 located in the space between the outer ring 10 and the inner ring 20 cannot be thickened relative to a standard bearing, the bending rigidity of the ring portion 31 may be insufficient. In this case, as shown by arrow A in FIG. 6, due to the centrifugal force acting on the column portion 32 of the retainer 30 when the bearing is used, the front end of the column portion 32 expands outward in the radial direction, and the corner portion 35 is easy to The direction of the week has expanded. Therefore, the movement amount ΔA in the axial direction of the holder 30 becomes large. When the movement amount ΔA in the axial direction of the retainer 30 becomes large, the axial distance ΔS1 between the retainer 30 and the inner ring 20 becomes narrower, and the possibility that the retainer 30 and the inner ring 20 interfere with each other becomes higher. . When it is assumed that the side surface of the pillar portion 32 viewed from the circumferential direction is not the shape of the second linear shape portion 33c, the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 becomes narrow, and the retainer 30 and The possibility that the inner rings 20 interfere with each other becomes high. Therefore, as in the angular ball bearing 1 of this embodiment, the second linear shape portion 33c is formed on the side surface of the column portion 32 when viewed from the circumferential direction, so that the axial distance Δ between the retainer 30 and the inner ring 20 can be further increased. S1, and the possibility that the retainer 30 and the inner ring 20 interfere with each other can be reduced.
又,本實施形態之斜角滾珠軸承1係為了增大軸向載荷負荷能力,而以增加滾珠3之數量(滾珠數量Z)之方式設定。更具體而言,使用圖11進行說明。於圖11中,顯示有配置於直徑dm之節圓上之二個滾珠3,且將該等滾珠3之直徑設為Dw,該等滾珠3之中心設為A、B,線段AB與滾珠3表面之交點設為C、D,線段AB之中點設為E,節 圓之中心設為O。又,將相鄰之滾珠3之中心A、B彼此之距離(線段AB之距離)即滾珠中心間距離設為T,相鄰之滾珠3彼此之距離(線段CD之距離)即滾珠間距離設為L,線段EO與線段BO所成角度(線段EO與線段AO所成角度)設為θ。如此,線段AO及線段BO之距離係(dm/2),滾珠中心間距離T為(dm×sinθ),滾珠間距離L為(T-Dw),角度θ為(180°/Z)。 In addition, the angular ball bearing 1 of this embodiment is set so as to increase the number of balls 3 (the number of balls Z) in order to increase the axial load capacity. More specifically, it demonstrates using FIG. 11. In FIG. 11, two balls 3 arranged on a pitch circle with a diameter of dm are shown. The diameter of the balls 3 is set to Dw, the centers of the balls 3 are set to A and B, and the line segments AB and the balls 3 are shown. The intersection of the surface is set to C, D, the midpoint of the line segment AB is set to E, and the node The center of the circle is set to O. In addition, the distance between the centers A and B of the adjacent balls 3 (the distance between the line segments AB), that is, the distance between the center of the balls is set to T, and the distance between the adjacent balls 3 (the distance of the line CD), that is, the distance between the balls is set. Is L, and the angle formed by the line segment EO and the line segment BO (the angle formed by the line segment EO and the line segment AO) is set to θ. In this way, the distance between the line segment AO and the line segment BO is (dm / 2), the distance T between the centers of the balls is (dm × sinθ), the distance L between the balls is (T-Dw), and the angle θ is (180 ° / Z).
且,滾珠間距離L、與圓周率π乘以滾珠節圓直徑dm所得之滾珠節圓周長πdm之間,以使2.5×10-3≦L/πdm≦13×10-3之關係成立之方式設計。假設L/πdm小於2.5×10-3,則保持器30之柱部32之圓周方向壁厚變得過薄,導致成形或切削時穿孔。尤其在含有較多強化材料時,成形時保持器30之材料即合成樹脂之流動性變差,容易穿孔。又,若L/πdm大於13×10-3,則滾珠數量Z變少,且軸承之軸向載荷負荷能力及剛性變低。 The distance L between the balls and the circumference πdm of the ball pitch obtained by multiplying the π by the ball pitch circle diameter dm is designed so that the relationship of 2.5 × 10 -3 ≦ L / πdm ≦ 13 × 10 -3 is established. . Assuming that L / πdm is less than 2.5 × 10 -3 , the wall thickness in the circumferential direction of the pillar portion 32 of the retainer 30 becomes too thin, resulting in perforation during forming or cutting. In particular, when a large amount of reinforcing material is contained, the fluidity of the synthetic resin, that is, the material of the holder 30 during molding is deteriorated, and perforation is easy. In addition, if L / πdm is larger than 13 × 10 -3 , the number of balls Z becomes small, and the axial load capacity and rigidity of the bearing become low.
如此,斜角滾珠軸承1係以滿足2.5×10-3≦L/πdm≦13×10-3之方式,即,以使滾珠數量Z較多之方式設計,且保持器30之柱部32之圓周方向壁厚無法相對於標準軸承加厚。因此,隨著柱部32之圓周方向壁厚變薄,角部35之壁厚變薄。因此,如圖6之箭頭A所示,滾珠3與保持器30之角部35碰撞時,角部35容易於周方向擴大,其結果使保持器之軸方向移動量△A變大。藉此,保持器30與內環20之間之軸方向距離△S1變窄,且保持器30與內環20彼此干涉之可能性變高。在假設柱部32之自周方向觀察之側面為不具有第2直線形狀部33c之形狀之情形時,保持器30與內環20之間之軸方向距離△S1變窄,且保持器30與內環20彼此干涉之可能性變高。因此,如本實施形態之斜角滾珠軸承1,藉由柱部32之自周方向觀察之側面具有第2直線形狀部33c,可進一步擴大保持器30與內環20之間之軸方向距離△S1,且可降低保持器30與內環20彼此干涉之可能性。 In this way, the angular ball bearing 1 is designed to satisfy 2.5 × 10 -3 ≦ L / πdm ≦ 13 × 10 -3 , that is, designed so that the number of balls Z is large, and the size of the column portion 32 of the retainer 30 The circumferential wall thickness cannot be thickened compared to standard bearings. Therefore, as the wall thickness in the circumferential direction of the pillar portion 32 becomes thinner, the wall thickness in the corner portion 35 becomes thinner. Therefore, as shown by arrow A in FIG. 6, when the ball 3 collides with the corner portion 35 of the retainer 30, the corner portion 35 tends to expand in the circumferential direction, and as a result, the axial movement amount ΔA of the retainer becomes large. Thereby, the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 becomes narrow, and the possibility that the retainer 30 and the inner ring 20 interfere with each other becomes high. When it is assumed that the side surface of the pillar portion 32 viewed from the circumferential direction is not the shape of the second linear shape portion 33c, the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 becomes narrow, and the retainer 30 and The possibility that the inner rings 20 interfere with each other becomes high. Therefore, like the angular ball bearing 1 of this embodiment, the second linear shape portion 33c is provided on the side surface of the column portion 32 when viewed from the circumferential direction, and the axial distance Δ between the retainer 30 and the inner ring 20 can be further increased. S1, and the possibility that the retainer 30 and the inner ring 20 interfere with each other can be reduced.
如圖12所示,即使在將柱部32之自周方向觀察之側面設為先前型之任意半徑r1之圓狀之情形時,亦與上述本實施形態之保持器30相同,於軸承之旋轉中,保持器30之軸方向相對移動量△A變大。且,於柱部32之自周方向觀察之側面為圓狀之情形時,如圖15所示,凹穴部33之引導滾珠3之部分即徑方向內側端部33d與滾珠3成點接觸。於該情形時,如圖13所示,凹穴部33之徑方向內側端部33d與滾珠3之間之徑方向距離為保持器30之徑方向移動量△R。 As shown in FIG. 12, even when the side surface of the column portion 32 viewed from the circumferential direction is set to a circular shape with an arbitrary radius r1 of the previous type, it is the same as the retainer 30 of this embodiment described above. In the middle, the relative movement amount ΔA in the axial direction of the holder 30 becomes larger. In addition, when the side surface of the pillar portion 32 viewed from the circumferential direction is round, as shown in FIG. 15, the radial direction inner end portion 33 d of the recessed portion 33 that guides the ball 3 is in point contact with the ball 3. In this case, as shown in FIG. 13, the radial distance between the radial inner end portion 33 d of the pocket portion 33 and the ball 3 is the radial movement amount ΔR of the retainer 30.
於該情形時,由於保持器30與滾珠3係點接觸,故於軸承旋轉中,保持器30對於內環20或外環10容易於軸方向相對移動,其結果亦使凹穴部33之徑方向內側端部33d之位置於軸方向移動。於圖12中,以一點鏈線表示於軸方向移動之凹穴部33(柱部32)。如此,凹穴部33之徑方向內側端部33d與滾珠3之間之徑方向距離與朝軸方向移動前相比,移動後變得更大,因此保持器30之徑方向移動量△R與朝軸方向移動前(參照圖13)相比,移動後(參照圖14)亦變得更大。 In this case, since the retainer 30 is in point contact with the ball 3, during the bearing rotation, the retainer 30 is relatively easy to move relative to the axial direction of the inner ring 20 or the outer ring 10, and as a result, the diameter of the cavity portion 33 is also reduced. The position of the direction inner end portion 33d moves in the axial direction. In FIG. 12, the concave portion 33 (the pillar portion 32) that moves in the axial direction is indicated by a one-dot chain line. In this way, the radial distance between the inner end portion 33d in the radial direction of the pocket portion 33 and the ball 3 becomes larger after the movement than before the movement in the axial direction. Therefore, the radial movement amount ΔR of the retainer 30 and Compared with the movement in the axial direction (see FIG. 13), the movement is also larger after the movement (see FIG. 14).
由於該現象係每次在保持器30對於內環20或外環10於軸方向相對移動時發生,故於柱部32之自周方向觀察之側面為圓狀之情形時,無法穩定引導滾珠3,且保持器30之振動增加,產生保持器音或保持器30提前破損等之問題。 Since this phenomenon occurs each time the retainer 30 moves relative to the inner ring 20 or the outer ring 10 in the axial direction, the ball 3 cannot be guided stably when the side surface of the column portion 32 viewed from the circumferential direction is round. Moreover, the vibration of the holder 30 increases, which causes problems such as a holder sound or the holder 30 being damaged in advance.
因此,如本實施形態,藉由於柱部32之自周方向觀察之側面設置第1直線形狀部33b,而設為如圖16所示,凹穴部33之引導滾珠3之部分即第1直線形狀部33b、與滾珠3以圓弧狀進行線接觸之構成。如此,藉由將保持器30與滾珠3之接觸部分設為線接觸,在保持器30於徑方向移動時,滾珠3靈活地卡入凹穴部33,可抑制保持器30之軸方向相對移動。因此,可防止保持器30之徑方向移動量△R之變化,且可抑制軸承旋轉中振動之增加。又,保持器30之軸方向移動受抑制,其結果可抑制保持器音或保持器30提前破損等問題。 Therefore, as in the present embodiment, the first linear shape portion 33b is provided because the side surface of the pillar portion 32 is viewed from the circumferential direction, so as shown in FIG. 16, the first linear portion is the portion that guides the ball 3 of the cavity portion 33. The shape portion 33b is configured to make linear contact with the ball 3 in an arc shape. In this way, by making the contact portion between the retainer 30 and the ball 3 in line contact, when the retainer 30 moves in the radial direction, the ball 3 flexibly engages in the recessed portion 33, and the relative movement of the retainer 30 in the axial direction can be suppressed. . Therefore, a change in the radial movement amount ΔR of the retainer 30 can be prevented, and an increase in vibration during bearing rotation can be suppressed. In addition, the axial movement of the holder 30 is suppressed, and as a result, problems such as the holder sound or the damage of the holder 30 in advance can be suppressed.
在將柱部32之自周方向觀察之側面設為圓狀之情形(參照圖12)時,除上述之軸承旋轉中產生之問題以外,亦存在可能產生之問題。該問題係指因保持器30之凹穴部33之節圓位置、與滾珠3之節圓位置於軸方向相對偏移,故保持器30之徑方向移動量△R脫離設計上之範圍而變化,而難以進行保持器製造時之滾珠外接圓徑及滾珠內接圓徑之正確測定。 When the side surface of the pillar portion 32 viewed from the circumferential direction is rounded (see FIG. 12), in addition to the problems caused during the rotation of the bearing described above, there may be problems. This problem refers to the fact that the pitch circle position of the recessed portion 33 of the retainer 30 and the pitch circle position of the ball 3 are relatively offset from each other in the axial direction, so the radial movement amount ΔR of the retainer 30 varies from the designed range. , And it is difficult to accurately measure the outer diameter of the ball and the inner diameter of the ball when the cage is manufactured.
作為保持器30之滾珠外接圓徑及滾珠內接圓徑之測定方法之一,有於將保持器30之環部31設於下之狀態,對徑方向內側賦予較輕之測定載荷而固定滾珠3進行測定之方法。此時,凹穴部33內之滾珠3係因重力而於凹穴部33中向環部31側靠近。其結果,凹穴部33之節圓位置、與滾珠3之節圓位置係向軸方向相對偏移。且,保持器30之徑方向移動量△R相較於向軸方向移動前(參照圖13),移動後(參照圖14)變得較大,其結果導致徑方向移動量△R變大且超過設計上之範圍。於該情形時,難以進行保持器30之滾珠外接圓徑及滾珠內接圓徑之正確測定。 As one of the measuring methods of the outer diameter of the ball and the inner diameter of the ball in the cage 30, there is a state in which the ring portion 31 of the cage 30 is set down, and the ball is fixed with a lighter measurement load on the inner side in the radial direction. 3 Method of measurement. At this time, the ball 3 in the cavity portion 33 approaches the ring portion 31 side in the cavity portion 33 due to gravity. As a result, the pitch circle position of the pocket portion 33 and the pitch circle position of the ball 3 are relatively shifted in the axial direction. In addition, the radial movement amount ΔR of the retainer 30 is larger than that before the movement in the axial direction (see FIG. 13) after the movement (see FIG. 14). As a result, the radial movement amount ΔR becomes larger and Beyond the scope of design. In this case, it is difficult to accurately measure the outer diameter of the ball and the inner diameter of the ball of the cage 30.
因此,於本實施形態中,於柱部32之自周方向觀察之側面設置第1直線形狀部33b,藉此如圖16所示,藉由測定載荷使滾珠3卡入第1直線形狀部33b之部分,而使滾珠3不於軸方向偏移,且令滾珠外接圓徑及滾珠內接圓徑之正確測定變得容易。 Therefore, in this embodiment, the first linear shape portion 33b is provided on the side surface of the pillar portion 32 as viewed from the circumferential direction. As shown in FIG. 16, the ball 3 is engaged with the first linear shape portion 33b by the measurement load. In this way, the ball 3 does not shift in the axial direction, and it is easy to accurately measure the outer diameter of the ball and the inner diameter of the ball.
另,凹穴部33之球面中心位置係不限於較環部31之最外徑部m1與最內徑部m2之徑方向中間位置M,偏移至徑方向內側之構成,亦可如圖17~19所示,為偏移至徑方向外側之構成。即,亦可採用於外環槽肩部12與內環埋頭孔23之間配置環部31,且於外環10及內環20之軌道面11、21間配置柱部32,並於柱部32之徑方向內側端部連接環部31之構造。另,於圖示之例中,凹穴部33之球面中心位置較環部31之最外徑部m1偏移至徑方向外側。於該情形時,亦因柱部32之前端於周 方向中間設置有缺口部34且分叉,故於以射出成型製造保持器30時,可防止因形成凹穴部33之模具零件之強制拔出而引起之柱部32之凹穴部33側之角部35之破損。 In addition, the spherical center position of the cavity portion 33 is not limited to the radial direction intermediate position M of the outermost diameter portion m1 and the innermost diameter portion m2 of the ring portion 31, and the structure is shifted to the inner side in the radial direction, as shown in FIG. 17 ~ 19 shows the structure shifted to the outside in the radial direction. That is, it is also possible to arrange the ring portion 31 between the outer ring groove shoulder portion 12 and the inner ring countersunk hole 23, and arrange the post portion 32 between the track surfaces 11, 21 of the outer ring 10 and the inner ring 20, and place the post portion The structure in which the inner end portion in the radial direction of 32 is connected to the ring portion 31. In the example shown in the figure, the spherical center position of the recessed portion 33 is shifted to the outside in the radial direction from the outermost diameter portion m1 of the ring portion 31. In this case, because the front end of the column 32 is in the periphery A notch portion 34 is provided in the middle of the direction and is bifurcated. Therefore, when the retainer 30 is manufactured by injection molding, it can prevent the cavity portion 33 side of the column portion 32 caused by the forced extraction of the mold part forming the cavity portion 33. The corner 35 is damaged.
此處,形成凹穴部33之柱部32之自周方向觀察之側面係將連結環部31之徑方向外側面(徑方向一側面)31b與徑方向內側面(徑方向另一側面)31a之圓弧33a之一部分切除而成者。圓弧33a之中心係以P表示,半徑係以r表示。 Here, the side surface viewed from the circumferential direction of the pillar portion 32 forming the cavity portion 33 connects the radial outer surface (radial side surface) 31 b and the radial inner surface (radial direction side surface) 31 a of the connecting ring portion 31. A part of the arc 33a is cut out. The center of the arc 33a is represented by P, and the radius is represented by r.
更具體而言,柱部32之自周方向觀察之側面包含:第1直線形狀部33b,其係以切除圓弧33a之徑方向外側端部(徑方向一側端部)且於軸方向延伸之方式形成。第1直線形狀部33b係配置於較圓之中心P更靠向正面側(反負荷側,圖19中左側)。又,第1直線形狀部33b係與滾珠3之中心Oi(凹穴部33之球面中心)於軸方向重疊。 More specifically, the side surface of the pillar portion 32 viewed from the circumferential direction includes a first linear shape portion 33b which is a radial direction outer end portion (radial direction side end portion) which is cut away from the arc 33a and extends in the axial direction. Way of forming. The first linear shape portion 33b is disposed closer to the front side (the counter-load side, the left side in FIG. 19) than the center P of the circle. The first linear shape portion 33b overlaps the center Oi of the ball 3 (the spherical surface center of the cavity portion 33) in the axial direction.
再者,柱部32之自周方向觀察之側面包含:第2直線形狀部33c,其係將圓弧33a之連結第1直線形狀部33b之背面側(負荷側,圖19中右側)之端部、與環部31之徑方向外側面31b之正面側之端部之部分切除而形成。因此,第2直線形狀部33c係設為隨著朝向背面側(環部31側)而朝向徑方向內側之直線形狀。 In addition, the side surface of the pillar portion 32 viewed from the circumferential direction includes a second linear shape portion 33c, which is an end of the back side (load side, right side in FIG. 19) connecting the arc 33a to the first linear shape portion 33b. The portion and the end portion on the front side of the radially outer side surface 31 b of the ring portion 31 are cut out and formed. Therefore, the second linear shape portion 33c has a linear shape toward the inner side in the radial direction as it goes toward the back side (the ring portion 31 side).
又,柱部32之自周方向觀察之側面包含:第3直線形狀部33g,其係以切除圓弧33a之徑方向內側端部(徑方向另一側端部)且於軸方向延伸之方式形成。第3直線形狀部33g形成於與環部31之徑方向內側面31a相同平面上,且與該徑方向內側面31a無階差地連接。 In addition, the side surface of the column portion 32 viewed from the circumferential direction includes a third linear shape portion 33g which is formed by cutting the inner end portion (the other end portion in the radial direction) of the radial direction of the arc 33a and extending in the axial direction. form. The third linear shape portion 33 g is formed on the same plane as the radial inner surface 31 a of the ring portion 31 and is connected to the radial inner surface 31 a without a step.
如此,柱部32之自周方向觀察之側面成為連接有第3直線形狀部33g、圓弧33a、第1直線形狀部33b、及第2直線形狀部33c之形狀。 In this way, the side surface of the pillar portion 32 viewed from the circumferential direction has a shape in which the third linear shape portion 33g, the arc 33a, the first linear shape portion 33b, and the second linear shape portion 33c are connected.
於此種構成之情形時,亦可獲得與上述實施形態相同之效果。 In the case of such a configuration, the same effects as those of the above embodiment can be obtained.
其次,對變更第1實施形態之斜角滾珠軸承1之複數個參數之各實施例進行說明。 Next, each embodiment in which a plurality of parameters of the angular ball bearing 1 of the first embodiment is changed will be described.
於本實施形態之斜角滾珠軸承1中,將內徑設定為Φ15mm,接觸角α設定為50°,Ai(內環槽肩部22之徑方向高度Hi除以滾珠3之直徑Dw)之值設定為0.38,Ae(外環槽肩部12之徑方向高度He除以滾珠3之直徑Dw)之值設定為0.38。保持器30之材質係聚醯胺樹脂。滾珠間距離L、與圓周率π乘以滾珠節圓直徑dm所得之滾珠3節圓周長πdm之關係滿足L/πdm=12×10-3。 In the angular ball bearing 1 of this embodiment, the inner diameter is set to Φ15mm, the contact angle α is set to 50 °, and Ai (the height in the radial direction of the inner ring groove shoulder portion 22 divided by the diameter Dw of the ball 3) is a value The value is set to 0.38, and the value of Ae (the height He in the radial direction of the outer ring groove shoulder portion 12 divided by the diameter Dw of the ball 3) is set to 0.38. The material of the holder 30 is a polyamide resin. The relationship between the distance L between the balls and the circumference πdm of the three balls obtained by multiplying the pi by the ball pitch circle diameter dm satisfies L / πdm = 12 × 10 -3 .
藉由如此設定各參數,而確認獲得與上述實施形態相同之效果。 By setting each parameter in this way, it was confirmed that the same effect as that of the above embodiment can be obtained.
於本實施形態之斜角滾珠軸承1中,將內徑設定為Φ60mm,接觸角α設定為60°,Ai(內環槽肩部22之徑方向高度Hi除以滾珠3之直徑Dw)之值設定為0.47,Ae(外環槽肩部12之徑方向高度He除以滾珠3之直徑Dw)之值設定為0.47。保持器30之材質係基礎樹脂為聚縮醛樹脂,且添加10重量%之碳纖維作為強化材料者。滾珠間距離L、與圓周率π乘以滾珠節圓直徑dm所得之滾珠3節圓周長πdm之關係滿足L/πdm=2.3×10-3。 In the angular ball bearing 1 of this embodiment, the inner diameter is set to Φ60mm, the contact angle α is set to 60 °, and Ai (the height in the radial direction of the inner ring groove shoulder portion 22 divided by the diameter Dw of the ball 3) is a value The value is set to 0.47, and the value of Ae (the height He in the radial direction of the outer ring groove shoulder portion 12 divided by the diameter Dw of the ball 3) is set to 0.47. The material of the holder 30 is a polyacetal resin, and 10% by weight of carbon fiber is added as a reinforcing material. The relationship between the distance L between the balls and the circumference πdm of the three balls obtained by multiplying the pi by the ball pitch circle diameter dm satisfies L / πdm = 2.3 × 10 -3 .
藉由如此設定各參數,而確認獲得與上述實施形態相同之效果。 By setting each parameter in this way, it was confirmed that the same effect as that of the above embodiment can be obtained.
於本實施形態之斜角滾珠軸承1中,將內徑設定為Φ40mm,接觸角α設定為55°,Ai(內環槽肩部22之徑方向高度Hi除以滾珠3之直徑Dw)之值設定為0.43,Ae(外環槽肩部12之徑方向高度He除以滾珠3之直徑Dw)之值設定為0.43。保持器30之材質係基礎樹脂為聚醯胺樹脂,且添加20重量%之玻璃纖維作為強化材料者。滾珠間距離L、與圓周率π乘以滾珠節圓直徑dm所得之滾珠3節圓周長πdm之關係滿足 L/πdm=7.0×10-3。 In the angular ball bearing 1 of this embodiment, the inner diameter is set to Φ40mm, the contact angle α is set to 55 °, and the value of Ai (the height in the radial direction of the inner ring groove shoulder portion 22 divided by the diameter Dw of the ball 3) is The value is set to 0.43, and the value of Ae (the radial height He of the outer ring groove shoulder portion 12 divided by the diameter Dw of the ball 3) is set to 0.43. The material of the holder 30 is a polyamide resin, and 20% by weight of glass fiber is added as a reinforcing material. The relationship between the distance L between the balls and the circumference π dm of the three balls obtained by multiplying the pi by the ball pitch circle diameter dm satisfies L / πdm = 7.0 × 10 -3 .
藉由如此設定各參數,而確認獲得與上述實施形態相同之效果。 By setting each parameter in this way, it was confirmed that the same effect as that of the above embodiment can be obtained.
其次,對本發明之第2實施形態之斜角滾珠軸承進行說明。本實施形態之斜角滾珠軸承1係與第1實施形態比較,於保持器30未形成第1直線形狀部33b之構成上有所不同,其他之基本構成係大致相同。因此,藉由對相同或相等部分附註相同符號而省略或簡化說明,以下對不同部分進行詳述。 Next, an angular ball bearing according to a second embodiment of the present invention will be described. Compared with the first embodiment, the angular ball bearing 1 of this embodiment differs in the configuration in which the holder 30 does not form the first linear shape portion 33b, and other basic configurations are substantially the same. Therefore, by adding the same symbols to the same or equivalent parts and omitting or simplifying the description, the different parts will be described in detail below.
如圖20所示,本實施形態之形成凹穴部33之柱部32之自周方向觀察之側面係將連結環部31之徑方向內側面(徑方向一側面)31a與徑方向外側面(徑方向另一側面)31b之圓弧33a之一部分切除而成者。 As shown in FIG. 20, the side surface viewed from the circumferential direction of the pillar portion 32 forming the cavity portion 33 in this embodiment connects the inner side surface (radial side surface) 31a in the radial direction of the ring portion 31 and the outer side surface in the radial direction ( The other side of the radial direction) 31b is partially cut off.
更具體而言,柱部32之自周方向觀察之側面包含:第2直線形狀部33c,其係將連結圓弧33a之徑方向內側端部(徑方向一側端部,底部)33e、與環部31之徑方向內側面31a之部分的至少一部分切除而形成。於本實施形態中,第2直線形狀部33c以直線狀連結較圓弧33a之徑方向內側端部33e更靠向環部31側之起點X(第2直線形狀部33c與圓弧33a之交點)、與環部31之徑方向內側面31a之方式構成。另,第2直線形狀部33c亦可以連結圓弧33a之徑方向內側端部33e、與環部31之徑方向內側面31a之方式形成。即,亦可為第2直線形狀部33c之起點X、與圓弧33a之徑方向內側端部33e一致之構成。 More specifically, the side surface of the pillar portion 32 viewed from the circumferential direction includes a second linear shape portion 33c, which connects the radial inner end portion (radial side end portion, bottom portion) 33e of the circular arc 33a, and At least a part of the portion of the inner surface 31 a in the radial direction of the ring portion 31 is cut out and formed. In this embodiment, the second linear shape portion 33c is connected in a straight line to the starting point X (the intersection point of the second linear shape portion 33c and the arc 33a) closer to the ring portion 31 side than the inner end portion 33e in the radial direction of the arc 33a. ), And the inner side surface 31a of the radial direction of the ring part 31 is comprised. In addition, the second linear shape portion 33c may be formed so as to connect the radially inner end portion 33e of the circular arc 33a and the radially inner side surface 31a of the ring portion 31. That is, a configuration in which the starting point X of the second linear shape portion 33c coincides with the radially inner end portion 33e of the arc 33a may be adopted.
如以上般,本實施形態之柱部32之自周方向觀察之側面成為連接有圓弧33a、與第2直線形狀部33c之形狀。 As described above, the side surface of the pillar portion 32 in the present embodiment viewed from the circumferential direction has a shape in which the arc 33 a and the second linear shape portion 33 c are connected.
藉由如此於柱部32之自周方向觀察之側面形成第2直線形狀部33c,可進一步擴大保持器30與內環20之間之軸方向距離△S1(參照圖20),且可降低保持器30與內環20彼此干涉之可能性。即,可獲得與 第1實施形態相同之效果。例如,於圖10及圖22中,以一點鏈線示意性表示對保持器30負荷徑方向載荷F,且於徑方向彎曲之情形之形狀之一例。因保持器30於徑方向彎曲,導致保持器30之徑方向位置接近內環20側或外環10側。因此,保持器30與內環20之間之軸方向距離△S1變窄,且保持器30與內環20彼此干涉之可能性變高。在假設如圖12所示,柱部32之自周方向觀察之側面為不具有第2直線形狀部33c之圓狀之情形時,保持器30與內環20之間之軸方向距離△S1變窄,且保持器30與內環20彼此干涉之可能性變高。因此,如本實施形態之斜角滾珠軸承1,藉由於柱部32之自周方向觀察之側面形成第2直線形狀部33c,可進一步擴大保持器30與內環20之間之軸方向距離△S1,且可降低保持器30與內環20彼此干涉之可能性。 By forming the second linear shape portion 33c on the side surface viewed from the circumferential direction of the pillar portion 32 as described above, the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 can be further increased (see FIG. 20), and the retention can be reduced. Possibility that the device 30 and the inner ring 20 interfere with each other. That is, you get The same effect is obtained in the first embodiment. For example, in FIG. 10 and FIG. 22, an example of a shape in the case where the radial load F is applied to the retainer 30 and the radial direction load is shown with a one-dot chain line is shown. Since the retainer 30 is bent in the radial direction, the radial position of the retainer 30 is closer to the inner ring 20 side or the outer ring 10 side. Therefore, the axial distance ΔS1 between the retainer 30 and the inner ring 20 becomes narrow, and the possibility that the retainer 30 and the inner ring 20 interfere with each other becomes high. When it is assumed that, as shown in FIG. 12, the side surface of the pillar portion 32 viewed from the circumferential direction is circular without the second linear shape portion 33 c, the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 changes. It is narrow, and the possibility that the retainer 30 and the inner ring 20 interfere with each other becomes high. Therefore, as in the angular ball bearing 1 of this embodiment, the second linear shape portion 33c is formed on the side surface of the column portion 32 when viewed from the circumferential direction, so that the axial distance Δ between the retainer 30 and the inner ring 20 can be further increased. S1, and the possibility that the retainer 30 and the inner ring 20 interfere with each other can be reduced.
又,第2直線形狀部33c之起點X係位於較滾珠3之中心Oi(凹穴部33之球面中心),更靠向環部31側。藉由此種構成,由於可確保保持器30之柱部接觸內徑,即滾珠3與凹穴部33之接觸點內徑,故可將保持器30之徑方向移動量△R限制為適當之值。此處,滾珠引導方式之保持器30之徑方向移動量△R係如圖23所示,以凹穴部33之徑方向內側之滾珠3與凹穴部33之徑方向間隙△Ri、或徑方向外側之滾珠3與凹穴部33之徑方向間隙△Re之較小者決定{△R=min(△Re,△Ri)}。藉此,未使保持器30之徑方向移動量△R變大,可抑制保持器30與內環20之接觸。 The starting point X of the second linear shape portion 33c is located closer to the ring portion 31 side than the center Oi of the ball 3 (the spherical center of the cavity portion 33). With this configuration, since the inner diameter of the column portion of the retainer 30 can be ensured, that is, the inner diameter of the contact point between the ball 3 and the cavity portion 33, the radial movement amount ΔR of the retainer 30 can be limited to an appropriate value. Here, as shown in FIG. 23, the radial movement amount ΔR of the cage 30 of the ball guide method is the radial direction gap ΔRi between the ball 3 on the inner side in the radial direction of the pocket portion 33 and the pocket portion 33, or The smaller the radial clearance ΔRe between the ball 3 on the outer side of the direction and the cavity portion 33 is determined as {ΔR = min (ΔRe, ΔRi)}. Thereby, the radial movement amount ΔR of the retainer 30 is not increased, and the contact between the retainer 30 and the inner ring 20 can be suppressed.
另,本實施形態之斜角滾珠軸承1係如圖21所示,可並列組合使用,且與第1實施形態同樣設置外環倒角14及內環倒角24,藉此實現對內環20及外環10彼此干涉之防止、及油流通性之提高。 In addition, as shown in FIG. 21, the angular ball bearing 1 of this embodiment can be used side by side, and the outer ring chamfer 14 and the inner ring chamfer 24 are provided in the same manner as the first embodiment, thereby realizing the inner ring 20 Prevention of interference with the outer ring 10 and improvement of oil flowability.
另,凹穴部33之球面中心位置係不限於較環部31之最外徑部m1與最內徑部m2之徑方向中間位置M,偏移至徑方向內側之構成,亦可如圖24所示,為偏移至徑方向外側之構成。即,亦可採用於外環槽肩 部12與內環埋頭孔23之間配置環部31,且於外環10及內環20之軌道面11、21間配置柱部32,並於柱部32之徑方向內側端部連接環部31之構造。另,於圖示之例中,凹穴部33之球面中心位置係較環部31之最外徑部m1偏移至徑方向外側。於該情形時,柱部32之前端亦因於周方向中間設置有缺口部34,且分叉,故以射出成型製造保持器30時,可防止因形成凹穴部33之模具零件之強制拔出而引起之柱部32之凹穴部33側之角部35之破損。 In addition, the spherical center position of the cavity portion 33 is not limited to the radial direction intermediate position M of the outermost diameter portion m1 and the innermost diameter portion m2 of the ring portion 31, and the structure is offset to the inner side in the radial direction, as shown in FIG. 24. Shown is a configuration shifted to the outside in the radial direction. That is, it can also be used on the outer ring groove shoulder A ring portion 31 is arranged between the portion 12 and the inner ring countersunk hole 23, and a column portion 32 is arranged between the track surfaces 11 and 21 of the outer ring 10 and the inner ring 20, and the ring portion is connected to the inner end of the radial direction of the column portion 32 31 的 结构。 Structure of 31. In the example shown in the figure, the spherical center position of the pocket portion 33 is shifted to the outside in the radial direction from the outermost diameter portion m1 of the ring portion 31. In this case, the front end of the pillar portion 32 is also provided with a notch portion 34 in the middle in the circumferential direction and is bifurcated. Therefore, when the retainer 30 is manufactured by injection molding, it is possible to prevent forced extraction of the mold parts that form the cavity portion 33. The corner portion 35 on the side of the recessed portion 33 of the pillar portion 32 is caused by the damage.
此處,形成凹穴部33之柱部32之自周方向觀察之側面為將連結環部31之徑方向外側面(徑方向一側面)31b與徑方向內側面(徑方向另一側面)31a之圓弧33a之一部分切除而成者。圓弧33a之中心與滾珠3之中心Oi(凹穴部33之球面中心)一致,且半徑係以r表示。 Here, the side surface viewed from the circumferential direction of the pillar portion 32 forming the cavity portion 33 is the radial outer surface (radial direction one side) 31 b and the radial inner surface (radial direction other side) 31 a of the connecting ring portion 31. A part of the arc 33a is cut out. The center of the arc 33a is the same as the center Oi of the ball 3 (the center of the spherical surface of the concave portion 33), and the radius is represented by r.
更具體而言,柱部32之自周方向觀察之側面包含:第2直線形狀部33c,其係將連結圓弧33a之徑方向外側端部(徑方向一側端部)33f、與環部31之徑方向外側面31b之部分的至少一部分切除而形成。於本實施形態中,第2直線形狀部33c以直線狀連結較圓弧33a之徑方向外側端部33f更靠向環部31側之起點X(第2直線形狀部33c與圓弧33a之交點)、與環部31之徑方向外側面31b之方式構成。另,第2直線形狀部33c亦可以連結圓弧33a之徑方向外側端部33f、與環部31之徑方向外側面31b之方式形成。即,亦可為第2直線形狀部33c之起點X、與圓弧33a之徑方向外側端部33f一致之構成。 More specifically, the side surface of the pillar portion 32 viewed from the circumferential direction includes a second linear shape portion 33c, which connects the radial outer end portion (radial side end portion) 33f of the circular arc 33a and the ring portion. At least a part of the portion of the 31-direction radial outer surface 31b is cut out. In this embodiment, the second linear shape portion 33c is connected in a straight line to the starting point X (the intersection point of the second linear shape portion 33c and the arc 33a) closer to the ring portion 31 side than the outer end portion 33f in the radial direction of the arc 33a. ), And the radial outer surface 31b of the ring portion 31 is configured. The second linear shape portion 33c may be formed so as to connect the radially outer end portion 33f of the circular arc 33a and the radially outer side surface 31b of the ring portion 31. That is, the starting point X of the second linear shape portion 33c and the radial end portion 33f in the radial direction of the arc 33a may be configured.
如以上般,本實施形態之柱部32之自周方向觀察之側面成為連接有圓弧33a、與第2直線形狀部33c之形狀。 As described above, the side surface of the pillar portion 32 in the present embodiment viewed from the circumferential direction has a shape in which the arc 33 a and the second linear shape portion 33 c are connected.
如此,藉由於凹穴部33形成第2直線形狀部33c,可進一步擴大保持器30與外環10之間之軸方向距離△S2,且可降低保持器30與外環10彼此干涉之可能性。 In this way, by forming the second linear shape portion 33c by the recessed portion 33, the axial distance ΔS2 between the retainer 30 and the outer ring 10 can be further increased, and the possibility of interference between the retainer 30 and the outer ring 10 can be reduced. .
又,藉由將第2直線形狀部33c之起點X配置於較徑方向外側端部 33f更靠向環部31側,因可確保保持器30之柱部接觸外徑,即滾珠3與凹穴部33之接觸點外徑,故可將保持器30之徑方向移動量△R限制為適當之值。藉此,未使保持器30之徑方向移動量△R變大,可抑制保持器30與外環10之接觸。 In addition, the starting point X of the second linear shape portion 33c is arranged at the outer end portion in the radial direction. 33f is closer to the ring portion 31 side, because the outer diameter of the pillar portion of the retainer 30 can be ensured, that is, the outer diameter of the contact point between the ball 3 and the cavity portion 33, the radial movement amount ΔR of the retainer 30 can be limited Is an appropriate value. Thereby, the radial movement amount ΔR of the holder 30 is not increased, and the contact between the holder 30 and the outer ring 10 can be suppressed.
其次,對變更第2實施形態之斜角滾珠軸承1之複數個參數之各實施例進行說明。 Next, each embodiment in which a plurality of parameters of the angular ball bearing 1 of the second embodiment is changed will be described.
於本實施形態之斜角滾珠軸承1中,將內徑設定為Φ15mm,接觸角α設定為50°,Ai(內環槽肩部22之徑方向高度Hi除以滾珠3之直徑Dw)之值設定為0.38,Ae(外環槽肩部12之徑方向高度He除以滾珠3之直徑Dw)之值設定為0.38。保持器30之材質係聚醯胺樹脂。滾珠間距離L、與圓周率π乘以滾珠節圓直徑dm所得之滾珠3節圓周長πdm之關係滿足L/πdm=12×10-3。 In the angular ball bearing 1 of this embodiment, the inner diameter is set to Φ15mm, the contact angle α is set to 50 °, and Ai (the height in the radial direction of the inner ring groove shoulder portion 22 divided by the diameter Dw of the ball 3) is a value The value is set to 0.38, and the value of Ae (the height He in the radial direction of the outer ring groove shoulder portion 12 divided by the diameter Dw of the ball 3) is set to 0.38. The material of the holder 30 is a polyamide resin. The relationship between the distance L between the balls and the circumference πdm of the three balls obtained by multiplying the pi by the ball pitch circle diameter dm satisfies L / πdm = 12 × 10 -3 .
藉由如此設定各參數,而確認防止保持器30與內環20或外環10之接觸。 By setting the parameters in this way, it is confirmed that the holder 30 is prevented from coming into contact with the inner ring 20 or the outer ring 10.
於本實施形態之斜角滾珠軸承1中,將內徑設定為Φ60mm,接觸角α設定為60°,Ai(內環槽肩部22之徑方向高度Hi除以滾珠3之直徑Dw)之值設定為0.47,Ae(外環槽肩部12之徑方向高度He除以滾珠3之直徑Dw)之值設定為0.47。保持器30之材質係基礎樹脂為聚縮醛樹脂,且添加10重量%之碳纖維作為強化材料者。滾珠間距離L、與圓周率π乘以滾珠節圓直徑dm所得之滾珠3節圓周長πdm之關係滿足L/πdm=2.3×10-3。 In the angular ball bearing 1 of this embodiment, the inner diameter is set to Φ60mm, the contact angle α is set to 60 °, and Ai (the height in the radial direction of the inner ring groove shoulder portion 22 divided by the diameter Dw of the ball 3) is a value The value is set to 0.47, and the value of Ae (the height He in the radial direction of the outer ring groove shoulder portion 12 divided by the diameter Dw of the ball 3) is set to 0.47. The material of the holder 30 is a polyacetal resin, and 10% by weight of carbon fiber is added as a reinforcing material. The relationship between the distance L between the balls and the circumference πdm of the three balls obtained by multiplying the pi by the ball pitch circle diameter dm satisfies L / πdm = 2.3 × 10 -3 .
藉由如此設定各參數,而確認防止保持器30與內環20或外環10之接觸。 By setting the parameters in this way, it is confirmed that the holder 30 is prevented from coming into contact with the inner ring 20 or the outer ring 10.
於本實施形態之斜角滾珠軸承1中,將內徑設定為Φ40mm,接觸角設定為55°,Ai(內環槽肩部22之徑方向高度Hi除以滾珠3之直徑Dw)之值設定為0.43,Ae(外環槽肩部12之徑方向高度He除以滾珠3之直徑Dw)之值設定為0.43。保持器30之材質係基礎樹脂為聚醯胺樹脂,且添加20重量%之玻璃纖維作為強化材料者。滾珠間距離L、與圓周率π乘以滾珠節圓直徑dm所得之滾珠3節圓周長πdm之關係滿足L/πdm=7.0×10-3。 In the angular ball bearing 1 of this embodiment, the inner diameter is set to Φ40mm, the contact angle is set to 55 °, and the value of Ai (the height in the radial direction of the inner ring groove shoulder portion 22 divided by the diameter Dw of the ball 3) is set. It is 0.43, and the value of Ae (the radial height He of the outer ring groove shoulder portion 12 divided by the diameter Dw of the ball 3) is set to 0.43. The material of the holder 30 is a polyamide resin, and 20% by weight of glass fiber is added as a reinforcing material. The relationship between the distance L between the balls and the circumference π dm of the three balls obtained by multiplying the pi by the ball pitch circle diameter dm satisfies L / πdm = 7.0 × 10 -3 .
藉由如此設定各參數,而確認防止保持器30與內環20或外環10之接觸。 By setting the parameters in this way, it is confirmed that the holder 30 is prevented from coming into contact with the inner ring 20 or the outer ring 10.
又,本發明係並非限定於上述實施形態者,可進行適當變更、改良等。 The present invention is not limited to those described in the above embodiments, and can be appropriately changed, improved, and the like.
又,本申請案係基於2014年3月19日申請之日本專利申請案2014-56627、2014年3月19日申請之日本專利申請案2014-56628、及基於2014年7月17日申請之專利合作條約之國際申請案PCT/JP2014/069091者,其內容係作為參照而併入於此。 Also, this application is based on the Japanese Patent Application 2014-56627 filed on March 19, 2014, the Japanese Patent Application 2014-56628 filed on March 19, 2014, and the patent based on July 17, 2014 For the international application PCT / JP2014 / 069091 of the cooperation treaty, the contents thereof are incorporated herein by reference.
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CN107939838A (en) * | 2017-12-26 | 2018-04-20 | 瓦房店轴承集团有限责任公司 | Half retainer of angular contact ball bearing radial bore circular arc pocket hole |
EP3744992B1 (en) * | 2018-01-26 | 2022-01-26 | Nsk Ltd. | Angular ball bearing |
CN108916222A (en) * | 2018-08-18 | 2018-11-30 | 哈尔滨轴承集团公司 | The mating flexible bearing structure of robot |
CN110307254B (en) * | 2019-08-03 | 2024-02-13 | 添佶轴承科技(浙江)有限公司 | Angular contact ball bearing retainer |
CN112059559B (en) * | 2020-09-17 | 2021-07-06 | 中国航发沈阳黎明航空发动机有限责任公司 | Joint ball seat turning and milling combined machining and inner spherical surface grinding method |
CN113153912A (en) * | 2021-03-19 | 2021-07-23 | 上海人本精密机械有限公司 | Precision assembled self-lubricating ball bearing |
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- 2015-03-19 JP JP2016508812A patent/JP6569663B2/en active Active
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WO2015141812A1 (en) | 2015-09-24 |
CN106104027B (en) | 2019-08-30 |
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KR101960144B1 (en) | 2019-03-19 |
JP6569663B2 (en) | 2019-09-04 |
KR20160122825A (en) | 2016-10-24 |
WO2015141021A1 (en) | 2015-09-24 |
JPWO2015141812A1 (en) | 2017-04-13 |
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