WO2013031248A1 - 油圧式無段変速機用スラスト軸受 - Google Patents

油圧式無段変速機用スラスト軸受 Download PDF

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Publication number
WO2013031248A1
WO2013031248A1 PCT/JP2012/051683 JP2012051683W WO2013031248A1 WO 2013031248 A1 WO2013031248 A1 WO 2013031248A1 JP 2012051683 W JP2012051683 W JP 2012051683W WO 2013031248 A1 WO2013031248 A1 WO 2013031248A1
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Prior art keywords
thrust bearing
inner ring
outer ring
continuously variable
variable transmission
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PCT/JP2012/051683
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English (en)
French (fr)
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千聡 立山
宮本　真人
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日本精工株式会社
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Priority to DE212012000166.2U priority Critical patent/DE212012000166U1/de
Priority to CN2012900000171U priority patent/CN203176171U/zh
Priority to US13/700,198 priority patent/US20130188901A1/en
Publication of WO2013031248A1 publication Critical patent/WO2013031248A1/ja

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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0644—Component parts
    • F03C1/0668—Swash or actuated plate
    • F03C1/0671—Swash or actuated plate bearing means or driven axis bearing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/146—Swash plates; Actuating elements
    • F04B1/148—Bearings therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2078—Swash plates
    • F04B1/2085—Bearings for swash plates or driving axles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
    • 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
    • F16C19/10—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for axial load mainly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H39/00—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution
    • F16H39/04—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit
    • F16H39/06—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type
    • F16H39/08—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type each with one main shaft and provided with pistons reciprocating in cylinders
    • F16H39/10—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type each with one main shaft and provided with pistons reciprocating in cylinders with cylinders arranged around, and parallel or approximately parallel to the main axis of the gearing
    • F16H39/14—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type each with one main shaft and provided with pistons reciprocating in cylinders with cylinders arranged around, and parallel or approximately parallel to the main axis of the gearing with cylinders carried in rotary cylinder blocks or cylinder-bearing members
    • 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
    • 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
    • F16C2240/60—Thickness, e.g. thickness of coatings
    • 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
    • F16C2310/00—Agricultural machines
    • 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
    • F16C2360/00—Engines or pumps
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/42—Pumps with cylinders or pistons
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/44—Centrifugal pumps

Definitions

  • the present invention relates to a thrust bearing for a hydraulic continuously variable transmission.
  • a thrust bearing is employed in a portion that receives piston pressure when converting the rotational force of the shaft into hydraulic pressure or when converting the hydraulic pressure into rotational force of the shaft (for example, Patent Document 1).
  • thrust bearings incorporated therein have also been miniaturized and used under high load conditions.
  • a large load is applied to the inner ring that comes into contact with the piston of the hydraulic continuously variable transmission of the thrust bearing, and it may be damaged in some cases.
  • the present invention has been made in view of the above circumstances, and an object of the present invention is to provide a thrust bearing for a hydraulic continuously variable transmission that prevents damage to the inner ring and has a long service life.
  • the present invention includes an inner ring that is incorporated in a hydraulic continuously variable transmission and contacts a piston in a piston chamber of a variable displacement pump, an outer ring that is fixed to a swash plate, an inner ring and an outer ring.
  • a thrust bearing comprising a plurality of rolling elements held via a cage in between, wherein the groove bottom thickness (Ti) of the inner ring is 40% or more of the ball diameter, and the groove bottom thickness (Te) of the outer ring is Provided is a thrust bearing for a hydraulic continuously variable transmission, characterized by having a ball diameter of 15% or more and a (Ti / Te) ratio of greater than 1 and 3 or less.
  • the upper limit of the groove bottom thickness (Ti) of the inner ring is 1.2 to 1.5 times 40% of the ball diameter
  • the upper limit of the groove bottom thickness (Te) of the outer ring is 1.2% of 15% of the ball diameter. It is preferable to be ⁇ 1.5 times.
  • the inner ring contacting the piston of the piston chamber of the variable capacity pump of the hydraulic continuously variable transmission is made thicker than the outer ring fixed to the swash plate. Even if it receives a high load due to, damage is suppressed and the service life is extended. Further, the height of the entire thrust bearing including the inner ring, the outer ring and the ball can be reduced, and space can be saved.
  • FIG. 1 is a cross-sectional view showing an example of a hydraulic continuously variable transmission mechanism.
  • a hydraulic continuously variable transmission 30 is a variable capacity that converts a rotational driving force transmitted from an engine (not shown) to an input shaft 31 into an oil pressure.
  • a pump 32 and a variable displacement motor 41 that returns the hydraulic pressure to the rotational driving force and transmits it to the output shaft 40 are provided, and the rotational driving force transmitted to the input shaft 31 is not used for the forward driving force and the backward driving force. It changes to a stage and outputs from the output shaft 40, or stops this output.
  • the variable displacement pump 32 includes a cylinder block 33 that rotates integrally with the input shaft 31, a nose piston 35 that is reciprocated in the piston chamber 34, and a guide surface of the guide block 36. And a swash plate 37 rotating along the axis.
  • the variable displacement pump 32 rotates the swash plate 37 to change the reciprocating stroke of the nose piston 35 and change the amount of oil discharged from the piston chamber 34.
  • the thrust bearing 10 is disposed on the swash plate 37 at a position where the thrust bearing 10 contacts the tip of the nose piston 35, and the thrust bearing 10 rotates together with the swash plate 37.
  • the thrust bearing 10 includes an inner ring 12 having an inner ring raceway surface 11 and an outer ring 14 having an outer ring raceway surface 13 facing each other, and between the inner ring raceway surface 11 and the outer ring raceway surface 13, A plurality of balls 15 which are rolling elements are arranged so as to be freely rollable. Furthermore, the thrust bearing 10 includes a cage 16 that holds a plurality of balls 15 at equal intervals in the circumferential direction.
  • the inner ring 12 is rotatable, and the tip of the nose piston 35 contacts the end surface 21 opposite to the surface on which the inner ring raceway surface 11 is formed.
  • the outer ring 14 is fixed to the swash plate 37. Therefore, the thrust bearing 10 receives a high load received from the nose piston 35 by the inner ring 12 and escapes to the outer ring 14 side fixed to the swash plate 37 via the ball 15.
  • the groove bottom thickness (Ti) of the inner ring 12 is 40% or more of the diameter (D) of the ball 15, and the groove bottom thickness (Te) of the outer ring 14 is 15% or more of the diameter (D) of the ball 15.
  • the (Ti / Te) ratio is greater than 1 and 3 or less.
  • the diameter (D) of the ball 15 is 14.288 mm
  • the load by the nose piston 35 is 790 kgf / cm 2
  • the groove bottom thickness (Ti) is 40% or more with respect to the diameter (D) of 15
  • the groove bottom thickness (Te) is 15% or more with respect to the diameter (D) of the ball 15 for the outer ring 14, and (Ti / When the Te) ratio was 2.67, it was calculated from the calculation of bending that the inner ring 12 and the outer ring 14 did not break.
  • the upper limit of the ratio of the groove bottom thickness (Ti) of the inner ring 12 and the groove bottom thickness (Te) of the outer ring 14 to the diameter (D) of the ball 15 is not limited. It only invites. Therefore, it is appropriate that the groove bottom thickness (Ti) of the inner ring 12 and the groove bottom thickness (Te) of the outer ring 14 are 1.2 to 1.5 times the minimum thickness described above.
  • the height (H) of the entire thrust bearing including the inner ring 12, the outer ring 14 and the ball 15 can be reduced, and space can be saved.
  • the groove bottom thickness (Ti) of the inner ring 12 is 40% of the diameter of the ball 15, and the groove bottom thickness (Te) of the outer ring 14 is set. If the diameter of the ball 15 is 15% and the (Ti / Te) ratio is 2.67, the inner ring 12 will be damaged with the same load even if the overall height (H) of the thrust bearing is reduced by 15%. Can be prevented.
  • the thrust bearing of the present invention is useful for agricultural machinery such as a combine, a tractor, a rice planting machine, and a lawn mower.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

　本発明は、油圧式無段変速機に組み込まれ、可変容量ポンプのピストン室のピストンと接触する内輪と、斜板に固定される外輪と、内輪と外輪との間に保持器を介して保持される複数の転動体とを備えるスラスト軸受であって、前記内輪の溝底厚（Ｔｉ）を玉径の４０％以上、前記外輪の溝底厚（Ｔｅ）を玉径の１５％以上、かつ、（Ｔｉ／Ｔｅ）比を１より大きく、３以下としたことを特徴とする。これにより、内輪の破損を防止して長寿命の油圧式無段変速機用スラスト軸受となる。

Description

油圧式無段変速機用スラスト軸受
　本発明は、油圧式無段変速機用スラスト軸受に関する。
　コンバインやトラクター、田植え機、芝刈り機等の農業機械では、ギアミッション方式から油圧式無段変速機への移行が進んでいる。このような油圧式無段変速機では、軸の回転力を油圧に変換させる際、または油圧を軸の回転力に変換させる際のピストン圧力を受ける部分に、スラスト軸受が採用されている（例えば特許文献１参照）。
日本国特開２００３－１９４１８３号公報
　近年、油圧式無段変速機の小型化に伴って、それに組み込まれるスラスト軸受も小型化され、高荷重条件下で使用されている。特に、スラスト軸受の油圧式無段変速機のピストンと当接する内輪には、大きな荷重が加わり、場合によっては破損することがある。
　本発明は上記事情に鑑みてなされたものであり、その目的は、内輪の破損を防止して長寿命の油圧式無段変速機用スラスト軸受を提供することにある。
　上記目的を達成するために、本発明は、油圧式無段変速機に組み込まれ、可変容量ポンプのピストン室のピストンと接触する内輪と、斜板に固定される外輪と、内輪と外輪との間に保持器を介して保持される複数の転動体とを備えるスラスト軸受であって、前記内輪の溝底厚（Ｔｉ）を玉径の４０％以上、前記外輪の溝底厚（Ｔｅ）を玉径の１５％以上、かつ、（Ｔｉ／Ｔｅ）比を１より大きく、３以下としたことを特徴とする油圧式無段変速機用スラスト軸受を提供する。また、内輪の溝底厚（Ｔｉ）の上限が玉径の４０％の１．２～１．５倍であり、外輪の溝底厚（Ｔｅ）の上限が玉径の１５％の１．２～１．５倍であることが好ましい。
　本発明の油圧式無段変速機用スラスト軸受では、油圧式無段変速機の可変容量ポンプのピストン室のピストンと接触する内輪を、斜板に固定される外輪よりも厚肉にしたため、ピストンによる高荷重を受けても破損が抑えられ、長寿命となる。また、内輪、外輪及び玉を合わせたスラスト軸受全体の高さを薄くすることもでき、省スペース化を図ることもできる。
油圧式無段変速機の一例を示す断面図である。 本発明のスラスト軸受を示す断面図である。
　以下、図面を参照して、本発明の油圧式無段変速機用スラスト軸受について詳細に説明する。
　図１は油圧式無段変速機構の一例を示す断面図であるが、油圧式無段変速機３０は、図示しないエンジンから入力軸３１に伝達された回転駆動力を油圧力に変換する可変容量ポンプ３２と、油圧力を回転駆動力に戻して出力軸４０に伝達する可変容量モータ４１とを備えており、入力軸３１に伝達された回転駆動力を前進側、後進側の駆動力に無段階に変更して出力軸４０から出力したり、この出力を停止したりする。
　可変容量ポンプ３２は、入力軸３１と一体回動するシリンダブロック３３と、シリンダブロック３３の周方向複数箇所に配置され、ピストン室３４内を往復動するノーズピストン３５と、ガイドブロック３６のガイド面に沿って回動する斜板３７とを備えている。可変容量ポンプ３２は、斜板３７が回動操作することで、ノーズピストン３５の往復動ストロークを変化し、ピストン室３４が吐出する油量を変化している。斜板３７には、スラスト軸受１０がノーズピストン３５の先端部と接触する位置に配置されており、スラスト軸受１０は斜板３７と共に回動する。
　スラスト軸受１０は、図２に示すように、内輪軌道面１１を有する内輪１２と、外輪軌道面１３を有する外輪１４とを対向配置し、内輪軌道面１１と外輪軌道面１３との間に、転動体である複数の玉１５を転動自在に配置したものである。さらに、スラスト軸受１０は、複数の玉１５を円周方向に亘って等間隔に保持する保持器１６を備える。
　また、内輪１２は回転可能であり、内輪軌道面１１が形成された面とは反対側の端面２１にノーズピストン３５の先端部が接触する。一方、外輪１４は、斜板３７に固定される。そのため、スラスト軸受１０はノーズピストン３５から受ける高荷重を内輪１２で受け、玉１５を介して、斜板３７に固定された外輪１４側へ逃がしている。
　本発明では、高荷重が加わる内輪１２を、外輪１４よりも厚肉にすることにより、ノーズピストン３５からの荷重に対する耐久性を高め、破損を防止する。具体的には、内輪１２の溝底厚（Ｔｉ）を玉１５の直径（Ｄ）の４０％以上とし、外輪１４の溝底厚（Ｔｅ）を玉１５の直径（Ｄ）の１５％以上とし、かつ、（Ｔｉ／Ｔｅ）比を１より大きく、３以下とする。
　上記の寸法は、内輪１２または外輪１４の両端を玉１５で支持し、ノーズピストン３５により荷重を負荷した梁を想定し、内輪１２及び外輪１４の材料や厚さ、荷重、曲げ応力の関係をシュミレーションして求めることができる。
　具体的には、内輪１２、外輪１４及び玉１５をＳＵＪ２製とし、玉１５の直径（Ｄ）を１４．２８８ｍｍとし、ノーズピストン３５による荷重を７９０ｋｇｆ／ｃｍ２としたとき、内輪１２については玉１５の直径（Ｄ）に対して溝底厚（Ｔｉ）を４０％以上、外輪１４については玉１５の直径（Ｄ）に対して溝底厚（Ｔｅ）を１５％以上、かつ、（Ｔｉ／Ｔｅ）比を２．６７としたときに、曲げの計算から内輪１２及び外輪１４が破断しないことを算出した。
　尚、内輪１２の溝底厚（Ｔｉ）及び外輪１４の溝底厚（Ｔｅ）とも、玉１５の直径（Ｄ）に対する比率の上限には制限はないが、必要以上に厚くしてもコスト増を招くだけである。そのため、内輪１２の溝底厚（Ｔｉ）及び外輪１４の溝底厚（Ｔｅ）ともに、上記した最小厚の１．２～１．５倍が適当である。
　また、上記の寸法とすることにより、内輪１２、外輪１４及び玉１５を合わせたスラスト軸受全体の高さ（Ｈ）を薄くすることもでき、省スペース化を図ることもできる。具体的には、内輪１２及び外輪１４を同じ溝底厚にした場合に比べて、内輪１２の溝底厚（Ｔｉ）を玉１５の直径の４０％、外輪１４の溝底厚（Ｔｅ）を玉１５の直径の１５％、かつ、（Ｔｉ／Ｔｅ）比を２．６７にした場合は、スラスト軸受全体の高さ（Ｈ）を１５％低減しても、同じ荷重で内輪１２の破損を防止することができる。
　本発明を詳細にまた特定の実施態様を参照して説明したが、本発明の精神と範囲を逸脱することなく様々な変更や修正を加えることができることは当業者にとって明らかである。
　本出願は、２０１１年８月２９日出願の日本特許出願（特願２０１１－１８６３６８）に基づくものであり、その内容はここに参照として取り込まれる。
　本発明のスラスト軸受は、コンバインやトラクター、田植え機、芝刈り機等の農業機械に有用である。
１０　スラスト軸受
１２　内輪
１４　外輪
１５　玉
１６　保持器
３５　ノーズピストン
３０　油圧式無段変速機
Ｔｉ　内輪の溝底厚
Ｔｅ　外輪の溝底厚

Claims (2)

  1. 　油圧式無段変速機に組み込まれ、可変容量ポンプのピストン室のピストンと接触する内輪と、斜板に固定される外輪と、内輪と外輪との間に保持器を介して保持される複数の転動体とを備えるスラスト軸受であって、
    　前記内輪の溝底厚（Ｔｉ）を玉径の４０％以上、前記外輪の溝底厚（Ｔｅ）を玉径の１５％以上、かつ、（Ｔｉ／Ｔｅ）比を１より大きく、３以下としたことを特徴とする油圧式無段変速機用スラスト軸受。
  2. 　内輪の溝底厚（Ｔｉ）の上限が玉径の４０％の１．２～１．５倍であり、外輪の溝底厚（Ｔｅ）の上限が玉径の１５％の１．２～１．５倍であることを特徴とする請求項１記載の油圧式無段変速機用スラスト軸受。
     
PCT/JP2012/051683 2011-08-29 2012-01-26 油圧式無段変速機用スラスト軸受 WO2013031248A1 (ja)

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DE212012000166.2U DE212012000166U1 (de) 2011-08-29 2012-01-26 Schublager für stufenloses Hydraulikgetriebe
CN2012900000171U CN203176171U (zh) 2011-08-29 2012-01-26 液压无级变速器用推力轴承
US13/700,198 US20130188901A1 (en) 2011-08-29 2012-01-26 Thrust bearing for hydraulic continuoulsy variable transmission

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JP6588242B2 (ja) * 2015-06-05 2019-10-09 Ntn株式会社 スラスト軸受用保持器およびスラスト軸受
JP6895207B2 (ja) * 2015-06-05 2021-06-30 Ntn株式会社 スラスト軸受用保持器およびスラスト軸受
DE112016002542T5 (de) * 2015-06-05 2018-02-15 Ntn Corporation Käfig für axiallager und axiallager

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