JPH0835912A - Frictional-wear testing apparatus - Google Patents
Frictional-wear testing apparatusInfo
- Publication number
- JPH0835912A JPH0835912A JP17408794A JP17408794A JPH0835912A JP H0835912 A JPH0835912 A JP H0835912A JP 17408794 A JP17408794 A JP 17408794A JP 17408794 A JP17408794 A JP 17408794A JP H0835912 A JPH0835912 A JP H0835912A
- Authority
- JP
- Japan
- Prior art keywords
- ball
- rotating
- rotating disk
- oil
- bearing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、試験片である回転球、
および回転円板によって玉軸受の転がり接触部をモデル
化し、高温、高速、高荷重等の条件下で、材料、潤滑剤
および潤滑方式により、モデル化された接触部における
摩擦や摩耗等の潤滑特性を評価するための摩擦摩耗試験
装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotating ball which is a test piece,
The rolling contact part of the ball bearing is modeled with a rotating disk and the lubrication characteristics such as friction and wear at the modeled contact part under the conditions of high temperature, high speed, high load, etc., depending on the material, lubricant and lubrication method. The present invention relates to a friction and wear test device for evaluating.
【０００２】[0002]
【従来の技術】図５、図６は、この種の、従来の摩擦摩
耗試験装置、及びその主要部分を示す図である。全体図
を示す図５において、カバー０１は、モータ０１２駆動
のポンプ０１３により、流量制御弁０１４、フィルタ０
１５、およびヒータ０１６を介して、油タンク０１１の
油が内部に注入されるとともに、モータ０１７駆動のポ
ンプ０１８により、フィルタ０１９を介して、内部の油
が油タンク０１１内に排油されて、その内部に高温、高
速の試験環境条件が設定されている。2. Description of the Related Art FIGS. 5 and 6 are views showing a conventional friction and wear test device of this type and its main part. In FIG. 5 showing the overall view, the cover 01 includes a flow rate control valve 014 and a filter 0 by a pump 013 driven by a motor 012.
The oil in the oil tank 011 is injected into the inside through the heater 15 and the heater 016, and the oil in the inside is discharged into the oil tank 011 through the filter 019 by the pump 018 driven by the motor 017. High temperature and high speed test environment conditions are set inside.
【０００３】このカバー０１の下方には、その上端部
を、カバー０１の底板を貫通して、カバー０１内部に突
出させたスピンドル０２１が立設されている。スピンド
ル０２１は、図示しない油圧モータ、又は電動モータに
より、その軸心まわりに回動するとともに、その下端部
には、油圧ピストン０２２を具えており、油圧ピストン
０２２、および下方に注、排出する作動油の油圧０２３
により、上下動できる機構となっている。Below the cover 01, there is provided a spindle 021 whose upper end penetrates the bottom plate of the cover 01 and projects into the inside of the cover 01. The spindle 021 is rotated about its axis by a hydraulic motor (not shown) or an electric motor, and has a hydraulic piston 022 at its lower end, and the hydraulic piston 022 and the operation of pouring and discharging downward Oil pressure 023
This makes it possible to move up and down.
【０００４】また、スピンドル０２１の上端部には、カ
バー０１の内部で、水平面内を回動し、玉軸受の軌道輪
を模擬する回転円板０２が固着されている。At the upper end of the spindle 021 is fixed a rotating disc 02 which rotates in a horizontal plane inside the cover 01 and simulates a bearing ring of a ball bearing.
【０００５】また、カバー０１の側部には、その先端部
を、カバー０１の側板を貫通させて、カバー０１内部に
突出させたスピンドル０３１が設けられている。スピン
ドル０３１は、水平面から傾斜角αの先端下りの傾斜に
設定されて、配設されるとともに、図示しない油圧モー
タ、又は電動モータにより、その軸心まわりに回動す
る。また、その後部に固着され、鉛直下方に垂下された
シリンダロッド０３３の下端部には、油圧機構０３２が
形成されており、下端部に作用する静圧０３４により、
シリンダロッド０３３を上、下動させて、先端下りの傾
斜角αを維持させたまま、スピンドル０３１を上下動で
きる機構にしている。A spindle 031 is provided on the side of the cover 01, the tip of which extends through the side plate of the cover 01 and protrudes into the cover 01. The spindle 031 is set so as to be inclined downward from the horizontal plane by an inclination angle α, and is rotated around its axis by a hydraulic motor or an electric motor (not shown). In addition, a hydraulic mechanism 032 is formed at the lower end of the cylinder rod 033 that is fixed to the rear part and hangs vertically downward, and due to the static pressure 034 acting on the lower end,
The mechanism is such that the cylinder rod 033 is moved up and down, and the spindle 031 can be moved up and down while maintaining the inclination angle α of the tip down.
【０００６】また、スピンドル０３１の先端部には、玉
軸受の回転する玉を模擬する回転球０３が固着されてお
り、この回転球０３はカバー０１の内部で、スピンドル
０３１軸心まわりに回動させられる。A rotating ball 03 simulating a rotating ball of a ball bearing is fixed to the tip of the spindle 031. The rotating ball 03 rotates inside the cover 01 about the spindle 031 axis. To be made.
【０００７】この種の摩擦摩耗試験装置においては、カ
バー０１内の詳細断面図である、図６に示すように、回
転球０３と回転円板０２の平面部０２４の間に、油圧ピ
ストン０２２による、スピンドル０２１を介しての回転
円板０２を上昇させる力と、油圧機構０３２による、ス
ピンドル０３１を下降させる力とによる荷重が、負荷さ
れて転がり接触し、この部分に生じる摩擦力や摩耗を検
出することによって、潤滑剤の潤滑特性や、転がり軸受
の構成材料の耐摩耗性・耐焼き付き性等を評価する構造
となっている。In this type of friction and wear test apparatus, as shown in FIG. 6, which is a detailed sectional view of the inside of the cover 01, a hydraulic piston 022 is provided between the rotating ball 03 and the flat portion 024 of the rotating disc 02. , The load by the force for raising the rotating disk 02 via the spindle 021 and the force by the hydraulic mechanism 032 for lowering the spindle 031 are loaded and make rolling contact, and the frictional force and wear generated in this part are detected. By doing so, the structure is such that the lubrication characteristics of the lubricant and the wear resistance and seizure resistance of the constituent materials of the rolling bearing are evaluated.
【０００８】しかしながら、上述した摩擦摩耗試験装置
においては、次に述べるような解決すべき問題点があっ
た。即ち、従来の摩擦摩耗試験装置では、上述したよう
に、回転球０３と回転円板０２の平面部０２４を押し付
けて試験を行うため、装置としては、玉軸受の回転球と
軌道輪（内輪および／又は外輪）との転がり接触部のモ
デル化を前提としているにもかかわらず、その接触部は
略真円形状となる。しかしながら、実際の玉軸受の接触
部形状は略楕円形状であるため、その転がり接触部に生
じる滑りの形態が、玉軸受で実際に生じるものとは異な
ったものとなっていた。However, the above-described frictional wear test apparatus has the following problems to be solved. That is, in the conventional friction and wear test device, as described above, the test is performed by pressing the rotating ball 03 and the flat surface portion 024 of the rotating disk 02, so that the device is a rotating ball and a bearing ring (inner ring and Although it is premised that the rolling contact part with the outer ring) is modeled, the contact part has a substantially perfect circular shape. However, since the actual contact part shape of the ball bearing is substantially elliptical, the form of slippage occurring in the rolling contact part is different from that actually occurring in the ball bearing.
【０００９】一般に、玉軸受に生じる滑りには、玉（回
転球）と軌道輪の巨視的な周速差により生じる公転滑り
と、玉と軌道輪との転がり接触部の微視的な周速差によ
って幾何学的に生じる滑りとがある。Generally, the slip that occurs in a ball bearing includes an orbital slip caused by a macroscopic peripheral speed difference between a ball (rotating ball) and a bearing ring, and a microscopic peripheral speed of a rolling contact portion between the ball and the bearing ring. There is a slip caused geometrically by the difference.
【００１０】このうち、公転滑りは、軌道輪から玉に作
用する駆動力が、油の攪拌等の回転抵抗より小さい場合
に、玉軸受の幾何学的寸法で定まる回転速度で、玉を軸
受内で公転させることができなくなって生じる。この滑
りは、軌道輪と玉との接触部全域で生じ、軸受荷重が小
さく、回転速度が大きい場合に発生し易い。潤滑状態に
もよるが、この滑りが激しいと、玉軸受の転走面（玉表
面、軌道輪みぞ表面）に摩耗等の損傷が生じる。Of these, the revolving slip means that when the driving force acting on the ball from the bearing ring is smaller than the rotational resistance such as oil agitation, the ball is moved inside the bearing at a rotational speed determined by the geometrical dimensions of the ball bearing. It occurs because it cannot be revolved around. This slippage occurs in the entire contact area between the bearing ring and the ball, and tends to occur when the bearing load is small and the rotation speed is high. Depending on the lubrication state, if this slippage is severe, the rolling surface (ball surface, raceway groove surface) of the ball bearing will be damaged, such as by abrasion.
【００１１】これに対し、玉と軌道輪との転がり接触部
の微視的な周速差によって幾何学的に生じる滑りには、
差動滑り、スピン滑り、ジャイロ滑りがある。On the other hand, the slip caused geometrically by the microscopic difference in peripheral speed of the rolling contact portion between the ball and the bearing ring is
There are differential slide, spin slide, and gyro slide.
【００１２】差動滑りは、図７（Ａ）に示すように、軌
道輪（内輪）の溝部の局所的な周速（内輪の表面速
度）、玉表面の局所的な周速（玉の表面速度）の差によ
って生じ、玉と軌道輪の溝部との間に滑りのない、純粋
の転がりが成立するのは２箇所に限られる。しかしなが
ら、この滑りは微少であり、玉軸受の焼き付きや、摩耗
といった不具合に直接結びつくことは一般に少ない。As shown in FIG. 7A, the differential slip is a local peripheral speed of the groove portion of the bearing ring (inner ring) (surface velocity of the inner ring) and a local peripheral speed of the ball surface (ball surface). There are only two places where a pure rolling without slip between the ball and the groove portion of the bearing ring is caused by the difference in speed). However, this slippage is very small, and in general, it is rarely directly linked to a defect such as seizure or wear of the ball bearing.
【００１３】また、スピン滑りは、玉の公転軸と自転軸
が一致しないアキシアル荷重を受ける玉軸受に生じ、玉
の自転軸角度によって、内輪側または外輪側、あるいは
その双方に発生し得る。たとえば、玉の自転軸が図７
（Ｂ）に示すような場合には、外輪と玉の接触部では、
上述の差動滑りのみが生じるが、内輪と玉の接触部で
は、差動滑りに加えて、玉と内輪が相対的に旋回する形
のスピン滑りが幾何学的に生じる。この滑りは、ガスタ
ービン主軸のように、高速、高アキシアル荷重条件にお
いて、玉軸受が用いられる場合、軸受の焼き付き、摩耗
等の不具合の原因となりうる。Spin slip occurs in a ball bearing that receives an axial load in which the revolution axis and the rotation axis of the ball do not coincide with each other, and may occur on the inner ring side or the outer ring side or both depending on the rotation axis angle of the ball. For example, the rotation axis of the ball is shown in Fig. 7.
In the case shown in (B), at the contact portion between the outer ring and the ball,
Although only the above-mentioned differential slip occurs, at the contact portion between the inner ring and the ball, in addition to the differential slip, a spin slip in which the ball and the inner ring relatively swivel geometrically occurs. When the ball bearing is used under the conditions of high speed and high axial load such as the gas turbine main shaft, this slippage may cause problems such as seizure and wear of the bearing.
【００１４】また、ジャイロ滑りもアキシアル荷重を受
ける玉軸受で発生する滑りである。すなわち、玉の公転
軸と自転軸が一致しない玉軸受の玉には、玉の自転、公
転角速度と玉の質量に比例したジャイロモーメントが作
用する。ここで、図７（Ｃ）に示すように、ジャイロモ
ーメントＭｇによって発生する接線力が、軌道輪の溝部
と玉との間に作用している転動体荷重Ｑに、接触面の摩
擦係数を乗じた値より大きくなると、ジャイロ滑りが発
生する。しかし、上述したスピン滑りが軸受荷重Ｑによ
らず発生するのに対し、ジャイロ滑りは、上述の発生機
構から、高アキシアル荷重では発生しにくい特徴があ
る。また、玉にジャイロ滑り運動が生じると、同時に玉
の自転軸角が玉の公転軸に平行になる方向に変化するた
めスピン滑りも増大する。このとき、玉と軌道輪の溝部
との間の滑りは、通常ジャイロ滑り成分よりもスピン滑
り成分のほうが大きくなる。Gyro slip is also slip that occurs in a ball bearing that receives an axial load. That is, a gyro moment proportional to the ball's rotation and revolution angular velocity and the mass of the ball acts on the ball of the ball bearing whose revolution axis and rotation axis do not match. Here, as shown in FIG. 7 (C), the tangential force generated by the gyro moment Mg multiplies the rolling element load Q acting between the groove portion of the bearing ring and the balls by the friction coefficient of the contact surface. Gyro-slip occurs when the value exceeds the specified value. However, while the above-mentioned spin slip occurs regardless of the bearing load Q, gyro slip has a characteristic that it is less likely to occur under a high axial load due to the above-described generation mechanism. Further, when a gyro-sliding motion occurs in the ball, at the same time, the spin axis angle of the ball changes in a direction parallel to the orbital axis of the ball, so that spin slip also increases. At this time, the slip between the balls and the groove of the race is usually larger in the spin slip component than in the gyro slip component.
【００１５】次に、図８に、スピン滑りで摩耗等の不具
合を生じ易い高速重アキシアル荷重下、および公転滑り
が生じ易い高速軽荷重下における、玉軸受の転がり接触
部の滑り速度Ｖ、接触面圧Ｐ、およびＰＶ値（滑り速度
と面圧の積）、並びに、それぞれの滑り状態で、潤滑が
不十分な場合に生じる接触部の典型的な摩耗形態をそれ
ぞれ示す。Next, FIG. 8 shows the sliding speed V and the contact speed of the rolling contact portion of the ball bearing under a high-speed heavy axial load where spin slipping is likely to cause problems such as wear and under a high-speed light load where revolution slipping is likely to occur. The surface pressures P and PV values (the product of the sliding speed and the surface pressure), and the typical wear forms of the contact portion that occur when lubrication is insufficient in each sliding state are shown.
【００１６】以上のことから、玉軸受の玉と軌道輪との
接触部を、モデル化し、潤滑剤の潤滑特性や転がり軸受
材の耐摩耗・耐焼き付き性を評価する場合には、上述の
公転滑りとスピン滑りを発生させられる摩擦摩耗試験装
置であることが必要であることが理解できよう。From the above, when the contact portion between the ball of the ball bearing and the bearing ring is modeled and the lubrication characteristics of the lubricant and the wear resistance and seizure resistance of the rolling bearing material are evaluated, It will be appreciated that it is necessary to have a friction and wear test device capable of producing slip and spin slip.
【００１７】しかしながら、従来のこの種の摩擦摩耗試
験装置においては、上述したように、回転円板０２の平
面部０２３に回転球０３を押し付ける構造であったた
め、公転滑りを発生させることはできるが、スピン滑り
速度、及びスピン滑りによるＰＶ値は、実際の玉軸受に
生じる量よりも非常に少なくなるという欠点があった。However, in the conventional friction and wear test device of this type, as described above, since the rotating ball 03 is pressed against the flat surface portion 023 of the rotating disc 02, revolving slip can be generated. However, the spin-sliding speed and the PV value due to the spin-sliding are much smaller than the amount actually generated in the ball bearing.
【００１８】また、従来の、この種の摩擦摩耗試験装置
において、評価可能な潤滑方法としては、固体潤滑剤の
場合には、固体潤滑剤を回転円板に押し付け潤滑部に移
着する方法、固体潤滑剤粉末を気体流で潤滑部に搬送す
る方法、あらかじめ固体潤滑剤を玉や平面部の接触部に
スパッタリング等で被膜する方法などがあり、液体潤滑
の場合は、滴下潤滑、オイルミスト潤滑、オイルエア潤
滑、及びジェット潤滑等がある。In the conventional friction and wear test apparatus of this type, as a lubrication method that can be evaluated, in the case of a solid lubricant, the solid lubricant is pressed against a rotating disk and transferred to a lubrication section, There is a method of transporting solid lubricant powder to the lubrication part by gas flow, a method of coating the solid lubricant in advance on the contact part of the ball or flat surface by sputtering, etc.In the case of liquid lubrication, drop lubrication, oil mist lubrication , Oil-air lubrication, jet lubrication, etc.
【００１９】しかし、高速玉軸受の有効な潤滑方法とし
て知られている、図９に示すアンダーレース潤滑はシミ
ュレートできない。したがって、とくに潤滑油の高温使
用限界付近の潤滑特性を評価する場合、玉と軌道輪接触
部（言い換えると玉軸受内部）に対する潤滑油量や、油
温の影響といった評価は可能であったが、アンダーレー
ス潤滑における給油点から軸受に至る油路において、油
量や油温の効果（例えば、スラッジの固着による流路の
閉塞、あるいは、遊離スラッジが転がり接触部の潤滑に
及ぼす影響）を評価することができなかった。However, the underrace lubrication shown in FIG. 9, which is known as an effective lubrication method for high speed ball bearings, cannot be simulated. Therefore, especially when evaluating the lubrication characteristics near the high temperature service limit of lubricating oil, it was possible to evaluate the amount of lubricating oil and the effect of oil temperature on the ball-raceway contact portion (in other words, inside the ball bearing). Evaluate the effect of oil amount and oil temperature in the oil passage from the oil supply point to the bearing in underrace lubrication (for example, the clogging of the passage due to sludge sticking or the effect of loose sludge on the lubrication of rolling contact parts) I couldn't.
【００２０】[0020]
【発明が解決しようとする課題】本発明は、従来の摩擦
摩耗試験装置の上述した不具合を解消するため、（１）
回転球と軌道輪との転がり接触部形状を楕円形状に模
擬でき、その転がり接触部の形態を、玉軸受で実際に生
じるものに近いものにでき、（２） 公転滑りを発生さ
せることができるばかりでなく、大きいスピン滑り速度
を発生させることができて、玉軸受に実際に生じる、ス
ピン滑りにより摩擦や摩耗を発生させることができ、
（３） 高速玉軸受の有効な潤滑方法である、アンダー
レース潤滑法における、評価が困難であった、給油点か
ら軸受に至る油路における、油温や油量の効果を確認で
き、潤滑剤による潤滑特性や、転がり軸受の構成材料の
耐摩耗性、耐焼き付き性を評価できるとともに、高温使
用限界付近の潤滑油による流路の閉塞、遊離スラッジの
転がり接触部への影響を評価できる、摩擦摩耗試験装置
を提供することを課題とする。SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems of the conventional friction and wear test apparatus by (1).
The shape of the rolling contact part between the rotating ball and the bearing ring can be simulated to an elliptical shape, and the form of the rolling contact part can be made close to what actually occurs in a ball bearing, and (2) revolving slip can be generated. Not only that, it can generate a high spin sliding speed, and can cause friction and wear due to the spin sliding that actually occurs in the ball bearing.
(3) The effect of oil temperature and oil amount in the oil passage from the oil supply point to the bearing, which was difficult to evaluate in the underrace lubrication method, which is an effective lubrication method for high-speed ball bearings, can be confirmed. It is possible to evaluate the lubrication characteristics, the wear resistance and the seizure resistance of the rolling bearing component materials, and to evaluate the influence of the lubricating oil near the high temperature service limit on the flow path and the effect of loose sludge on the rolling contact area. An object is to provide a wear test device.
【００２１】[0021]
【課題を解決するための手段】このため、本発明の摩擦
摩耗試験装置では、次の手段とした。 （１） 荷重が負荷されて回動する回転球を、回転円板
に設けられた曲面部に接触させて、回動させるようにし
た。Therefore, the frictional wear test apparatus of the present invention uses the following means. (1) A rotating ball, which is rotated by being loaded with a load, is brought into contact with a curved surface portion provided on a rotating disk to rotate the rotating ball.
【００２２】ここで、曲面部とは、回転円板の外周縁に
形成される円弧部も含むものとする。Here, the curved surface portion also includes an arc portion formed on the outer peripheral edge of the rotating disk.
【００２３】また、他の本発明の摩擦摩耗試験では、上
記（１）の手段に加え、次の手段とした。 （２） 前記（１）の曲面部は、回転円板の外周縁部、
若しくは回転円板の平面部に凹設された溝曲率部とし
た。In addition, in another friction and wear test of the present invention, the following means was used in addition to the above-mentioned means (1). (2) The curved surface portion of (1) is an outer peripheral edge portion of the rotating disk,
Alternatively, the curved surface of the rotating disk is formed as a concave groove.
【００２４】また、他の本発明の摩擦摩耗試験装置は、
上記（１）の手段に加え、又は上記（１）、（２）の手
段に加え、次の手段とした。 （３） ・回転円板の内部に、外部の潤滑油供給系から
供給される潤滑油を、一時貯留できる油溜まりを設け
た。Further, another friction wear test apparatus of the present invention is
In addition to the above means (1), or in addition to the above means (1) and (2), the following means is adopted. (3) An oil reservoir is provided inside the rotating disk to temporarily store the lubricating oil supplied from the external lubricating oil supply system.
【００２５】・回転円板の回転によって、油溜まりに貯
留された潤滑油に生じる遠心力を利用して、当該潤滑油
を、油溜まりから回転円板に設けられた曲面部に供給す
る油供給孔を回転円板の内部に穿設した。An oil supply that supplies the lubricating oil from the oil sump to the curved surface provided on the rotating disk by utilizing the centrifugal force generated in the lubricating oil stored in the oil sump by the rotation of the rotating disk. Holes were drilled inside the rotating disc.
【００２６】[0026]
【作用】本発明の摩擦摩耗試験装置は、上述（１）の手
段により、 （１） 接触部形状を、実際の玉軸受の玉と軌道輪で生
じる、略楕円形状のものにでき、従来の摩擦摩耗試験装
置で採用されている、回転球と平面部との接触により生
じるスピン滑りよりも、大きいスピン滑り速度を発生さ
せることができ、転がり接触部の滑り状態を実際の玉軸
受に近いものにできる。これにより、実際に近い状態の
潤滑剤による潤滑特性、転がり軸受の構成材料の耐摩耗
性、耐焼き付き性等の評価ができる。With the friction and wear test apparatus of the present invention, by means of the above-mentioned (1), (1) the contact portion can be formed into a substantially elliptical shape that occurs between the ball and the bearing ring of the actual ball bearing. A spin sliding speed that is higher than the spin sliding generated by the contact between a rotating ball and a flat surface, which is adopted in the friction and wear test equipment, and the sliding state of the rolling contact portion is closer to that of an actual ball bearing. You can As a result, it is possible to evaluate the lubrication characteristics of the lubricant in a state that is close to the actual state, the wear resistance of the constituent materials of the rolling bearing, the seizure resistance, and the like.
【００２７】また、本発明の摩擦摩耗試験装置は、上述
（２）の手段により、上述（１）に加え、 （２） 回転円板の表面に、回転球が接する溝曲率部を
設けたことにより、回転球と回転円板溝曲率部との接触
部形状が、実際の玉軸受の接触部と略同一の楕円形状と
なり、転がり接触部に生じるスピン滑り速度を、実際の
高速重アキシアル荷重下の玉軸受に生じるスピン滑り速
度と同程度に大きくすることができるとともに、スピン
滑りによるＰＶ値をモデル試験においても実現できるた
め、潤滑剤の潤滑特性や玉軸受構成材料の耐摩耗性・耐
焼き付き性について、従来のこの種の摩擦摩耗試験装置
に比べて、実際のものに略近い状態で評価することが可
能となる。In addition to the above-mentioned (1), the friction-wear test apparatus of the present invention has the above-mentioned (1), and (2) the surface of the rotating disk is provided with a groove curvature portion in contact with the rotating ball. As a result, the contact shape between the rotating sphere and the rotating disk groove curvature becomes an elliptical shape that is almost the same as the contact of the actual ball bearing, and the spin-sliding speed that occurs in the rolling contact is measured under the actual high-speed heavy axial load. Can be increased to the same level as the spin-sliding speed of ball bearings, and the PV value due to spin-sliding can also be realized in model tests, so the lubrication characteristics of the lubricant and wear resistance and seizure resistance of the ball bearing constituent materials can be achieved. It is possible to evaluate the performance in a state substantially closer to an actual one as compared with the conventional friction and wear test device of this type.
【００２８】また、本発明の摩擦摩耗試験装置は、上述
（３）の手段により、上述（１）、又は上述（１）、
（２）に加え、 （３） アンダーレース潤滑構造をシミュレートできる
油溜まりと、油供給孔を設けた回転円板を、回転球と転
がり接触させるようにしたので、モデル試験において、
実際のガスタービン、ジェットエンジン等の高速回転玉
軸受に用いられている、アンダーレース潤滑特性、とく
に、潤滑油の使用限界温度付近における特性評価が可能
となる。Further, the frictional wear test apparatus of the present invention is the above-mentioned (1) or the above-mentioned (1), by the above-mentioned (3) means.
(3) In addition to (2), (3) an oil reservoir that can simulate an underlaced lubrication structure and a rotating disk provided with an oil supply hole were brought into rolling contact with a rotating ball.
It is possible to evaluate the underrace lubrication characteristics used in high-speed rotating ball bearings of actual gas turbines, jet engines, etc., especially the characteristics near the operating temperature limit of the lubricating oil.
【００２９】[0029]
【実施例】以下、本発明の摩擦摩耗試験装置を実施例に
もとずき説明する。EXAMPLES Hereinafter, the frictional wear test apparatus of the present invention will be described based on Examples.
【００３０】図１は本発明の摩擦摩耗試験装置の第一実
施例を示す断面図、図２は第二実施例を示す断面図、図
３は第三実施例を示す断面図である。FIG. 1 is a sectional view showing a first embodiment of the friction and wear test apparatus of the present invention, FIG. 2 is a sectional view showing a second embodiment, and FIG. 3 is a sectional view showing a third embodiment.
【００３１】図１は、特許請求の範囲、請求項２に示す
発明の第一実施例である。図１に示すものは、玉軸受の
玉と、内輪軌道輪との転がり接触をモデル化したもので
あるが、複雑さを避けるため潤滑手段は図示していな
い。FIG. 1 shows a first embodiment of the invention shown in the claims and claim 2. 1 shows a model of rolling contact between a ball of a ball bearing and an inner ring bearing ring, but a lubricating means is not shown in order to avoid complexity.
【００３２】図において、図５に示されるものと同様
に、油タンクからの油が内部に注入され、又は内部に注
入された油を、油タンクに返すことにより、高温、高速
の試験環境が設定されたカバー１０の内部には、下方か
ら鉛直にカバー１０内に回転軸５が突設されており、回
転軸５の上端部には、回転円板２が固着されている。回
転軸５は下部に設けた、図示しない回転駆動手段により
回動し、固着した回転円板２を水平面内で回動させる。
また、回転円板２の外周縁には、モデル化を行う玉軸受
の内輪に設けられる溝と略同じ曲率にされた溝曲率部３
が形成されている。In the figure, similar to that shown in FIG. 5, the oil from the oil tank is injected into the inside, or the injected oil is returned to the oil tank, so that a high-temperature, high-speed test environment is created. Inside the set cover 10, a rotary shaft 5 is vertically projecting from below in the cover 10, and a rotary disc 2 is fixed to the upper end of the rotary shaft 5. The rotating shaft 5 is rotated by a rotation driving means (not shown) provided in the lower portion, and the fixed rotating disc 2 is rotated in a horizontal plane.
Further, on the outer peripheral edge of the rotating disk 2, a groove curvature portion 3 having a curvature substantially the same as the groove provided on the inner ring of the ball bearing to be modeled.
Are formed.
【００３３】一方、カバー１０の内部には、上方から、
鉛直軸とβの傾斜に設定された回転軸４が垂下されてい
る。また、回転軸４の先端は前記溝曲率部３に向けら
れ、回転球１が固着されている。回転軸４は、上方に設
けた図示しない回転駆動手段により回動し、先端に固着
した回転球１を軸まわりに回動する。回転駆動手段によ
って回転させた回転球１と、これも回転駆動手段によっ
て回転させた回転円板２の溝曲率部３との間には、図５
で示した回転円板の上下動機構、および回転球１を回動
する回転軸の移動機構と同等の方法により、荷重が負荷
される。On the other hand, inside the cover 10,
The rotary shaft 4 is set so as to be inclined with respect to the vertical axis and β. Further, the tip of the rotary shaft 4 is directed to the groove curvature portion 3, and the rotary ball 1 is fixed. The rotating shaft 4 is rotated by a rotation driving means (not shown) provided above the rotating shaft 4, and the rotating ball 1 fixed to the tip is rotated around the shaft. Between the rotary ball 1 rotated by the rotary drive means and the groove curvature portion 3 of the rotary disc 2 also rotated by the rotary drive means, as shown in FIG.
A load is applied by a method equivalent to the vertical movement mechanism of the rotating disc and the moving mechanism of the rotating shaft that rotates the rotating ball 1 shown in FIG.
【００３４】スピン滑りを発生させる場合には、回転球
１と溝曲率部３の接触部の周速度が巨視的に一致するよ
うに、回転球１と回転円板２の回転速度を、各々の軸
４、５で回転制御する。また、公転滑りを発生させる場
合には、所望の滑り速度に応じて回転球１と、回転円板
２の溝曲率部３との接触部周速が異なるように、お互い
の回転速度を制御する。When spin slip is generated, the rotational speeds of the rotating sphere 1 and the rotating disk 2 are adjusted so that the peripheral velocities of the contact portion between the rotating sphere 1 and the groove curvature portion 3 are macroscopically matched. The rotation is controlled by the shafts 4 and 5. Further, when revolving slip is generated, the rotational speeds of the rotating ball 1 and the groove curvature portion 3 of the rotating disc 2 are controlled so that the peripheral speeds of the contact portions of the rotating ball 1 and the groove curvature portion 3 of the rotating disk 2 differ depending on the desired sliding speed. .
【００３５】ここで、回転球１と溝曲率部３の巨視的な
周速度が一致するように、回転速度を制御したとき、回
転円板２の回転球１との接触表面が平面の場合（球／平
板平面）と、回転円板２に溝曲率部３が設けられた場合
（球／軌道溝）とについて、接触面に生じる最大接触面
圧Ｐ、スピン滑り速度Ｖ、接触面内に生じる最大スピン
ＰＶ値（スピン滑り速度と接触面圧の積の最大値）の計
算値を、表１に比較して示す。表１には、計算条件も同
時に示した。計算において、球材質は窒化けい素、平板
材質は耐熱軸受鋼としている。Here, when the rotation speed is controlled so that the macroscopic peripheral velocities of the rotating sphere 1 and the groove curvature portion 3 coincide with each other, the contact surface of the rotating disc 2 with the rotating sphere 1 is a flat surface ( Maximum contact surface pressure P generated on the contact surface, spin slip velocity V, and the inside of the contact surface in the case where the rotary disk 2 is provided with the groove curvature portion 3 (sphere / orbit groove). The calculated values of the maximum spin PV value (the maximum value of the product of the spin sliding speed and the contact surface pressure) are shown in comparison with Table 1. Table 1 also shows the calculation conditions. In the calculation, the ball material is silicon nitride and the flat plate material is heat-resistant bearing steel.
【００３６】[0036]
【表１】 [Table 1]
【００３７】実際のガスタービン用高速玉軸受において
は、通常最大スピン滑り速度は数 m／s 程度であり、最
大スピンＰＶ値は数百kgｆ／mm2 ・ m／s 程度であるこ
とが知られている。It is known that in actual high-speed ball bearings for gas turbines, the maximum spin slip velocity is usually about several m / s, and the maximum spin PV value is about several hundred kgf / mm 2 · m / s. ing.
【００３８】これに対して、表１から球／平板平面の場
合、最大スピン滑り速度は０．５ m／s 以下、最大スピ
ンＰＶ値は数拾kgｆ／mm2 ・ m／s であるのに対して、
球／軌道溝の場合、上述した、ガスタービン用高速玉軸
受における最大スピン滑り速度、および最大スピンＰＶ
値と同等の値を発生させることができ、回転円板２に溝
曲率部３を設け、回転球１と接触させるようにすること
によって、回転球１と溝曲率部３の接触部の滑りの状態
が、実際の高速重アキシアル荷重下の玉軸受における滑
り状態に近づけることができることがわかり、本実施例
による効果が良くわかる。On the other hand, from Table 1, in the case of a sphere / flat plate, the maximum spin slip velocity is 0.5 m / s or less and the maximum spin PV value is several kgf / mm 2 · m / s. for,
In the case of a sphere / raceway groove, the above-mentioned maximum spin sliding speed and maximum spin PV in the high-speed ball bearing for gas turbine are used.
It is possible to generate a value equivalent to the value, and by providing the rotating disk 2 with the groove curvature portion 3 so as to make contact with the rotating ball 1, slip of the contact portion between the rotating ball 1 and the groove curvature portion 3 can be prevented. It can be seen that the state can be brought close to an actual sliding state in the ball bearing under the high-speed heavy axial load, and the effect of the present embodiment can be clearly understood.
【００３９】次に、図２は、特許請求の範囲、請求項２
に示す発明の第二実施例である。本実施例では、鉛直に
立設された回転軸５の上端に固着され、カバー１０内部
で水平面内の回動を行う、回転円板２の中央部に凹所６
が形成されて、回転円板２の外周部に、第一実施例と同
様の曲率にされた、内向きの溝曲率部３′が形成されて
いる。また、カバー１０の側部からカバー１０内部に向
けて、先端下りαの傾斜角に設定された回転軸４が突出
されている。回転軸４の先端には、溝曲率部３′と接触
させ、回動させる回転球としての回転球１が固着されて
いる。Next, FIG. 2 shows claims and claim 2.
2 is a second embodiment of the invention shown in FIG. In this embodiment, a recess 6 is fixed to the upper end of a vertically standing rotating shaft 5 and rotates in a horizontal plane inside the cover 10 in the center of the rotating disk 2.
Is formed, and an inward groove curvature portion 3'having a curvature similar to that of the first embodiment is formed on the outer peripheral portion of the rotary disc 2. Further, the rotary shaft 4 set to have an inclination angle of the tip down α is projected from the side portion of the cover 10 toward the inside of the cover 10. At the tip of the rotating shaft 4, a rotating ball 1 is fixed as a rotating ball which is brought into contact with the groove curvature portion 3'to rotate.
【００４０】本実施例における作用、効果は、第一実施
例と同様であるが、本実施例の場合、回転球１を回動さ
せる回転軸４の設定が、図６に示す、従来装置と同じに
できるため、従来装置から、回転円板を図示のものに取
替えるだけで、回転球１と溝曲率部３′の接触部の滑り
部の状態を、実際の高速重アキシアル荷重下の玉軸受に
おける滑り状態にしたものを作り出すことができる。The operation and effect of this embodiment are similar to those of the first embodiment, but in the case of this embodiment, the setting of the rotary shaft 4 for rotating the rotary ball 1 is different from that of the conventional device shown in FIG. Since it can be made the same, the state of the sliding portion of the contact portion between the rotating ball 1 and the groove curvature portion 3'can be changed from the conventional device to the one shown in the figure, and the state of the sliding portion of the ball bearing under the actual high-speed heavy axial load Can be made to slip.
【００４１】次に、図３は特許請求の範囲請求項１に示
す発明の一実施例である。本実施例では、とくに回転円
板に溝曲率部を凹設せず、溝を設けてはいないが、回転
円板２の外周表面３″と回転球１とを接触させることに
よって、接触部形状を楕円形状にし、スピン滑りを、回
転球１と回転円板の平面部との接触の場合より増加させ
た例を示す。本実施例のように、回転球１を回転円板２
の平面部でなく、外周表面に形成された曲面部３″に接
触させることによっても、従来の装置に比べ実際の玉軸
受における滑りの状態に近づけることができる。Next, FIG. 3 shows an embodiment of the invention shown in Claim 1. In the present embodiment, in particular, the grooved curvature portion is not provided in the rotating disk and the groove is not provided. However, by contacting the outer peripheral surface 3 ″ of the rotating disk 2 with the rotating ball 1, the contact portion shape Shows an example in which the spin sphere 1 has an elliptical shape and the spin slip is increased more than in the case of contact between the rotating sphere 1 and the flat surface of the rotating disc.
By contacting the curved surface portion 3 ″ formed on the outer peripheral surface instead of the flat surface portion, it is possible to make the sliding state of the actual ball bearing closer to that of the conventional device.
【００４２】次に、図４は特許請求の範囲、請求項３に
示す発明の一実施例である。本実施例においては、回転
球１と転がり接触する回転円板２には、外部の潤滑油供
給系としての潤滑油供給ノズル７から供給される潤滑油
を、一時的に貯留する油溜まり８と、油溜まりに貯留さ
れた油を、回転球１と回転円板の曲面部との接触部近傍
に、回転遠心力によって導く油供給孔９が設けられてい
る。本実施例は、図５に示す如く、回転円板２の回転球
１との接触面を平面としたものにも適用することも可能
であり、また、油供給孔９を油溜まり８から回転円板２
外周面に連通させて、図１に示す、回転球１と回転円板
２との接触構造に適用することも当然可能である。Next, FIG. 4 shows an embodiment of the invention shown in claims and claim 3. In the present embodiment, the rotating disk 2 that makes rolling contact with the rotating ball 1 is provided with an oil pool 8 for temporarily storing the lubricating oil supplied from a lubricating oil supply nozzle 7 as an external lubricating oil supply system. An oil supply hole 9 that guides the oil stored in the oil sump by a rotating centrifugal force is provided near the contact portion between the rotating ball 1 and the curved surface portion of the rotating disk. As shown in FIG. 5, this embodiment can also be applied to one in which the contact surface of the rotating disk 2 with the rotating ball 1 is a flat surface, and the oil supply hole 9 is rotated from the oil sump 8 Disk 2
It is naturally possible to communicate with the outer peripheral surface and apply it to the contact structure between the rotating ball 1 and the rotating disk 2 shown in FIG.
【００４３】以上述べた実施例は、高速回転玉軸受用の
潤滑剤、潤滑法、および軸受材料の評価を行うために、
実際の玉軸受を回転させて評価するのではなく、より簡
便なモデル試験において、現実の玉軸受に生じる滑りを
実現して、評価するためになされたものである。したが
って、回転円板と回転球の材質、潤滑法、潤滑剤は評価
の必要に応じて変更可能であることは言うまでもない。
また、カバー内部に不活性ガス等の雰囲気ガスを圧送
し、大気雰囲気以外の雰囲気においても試験することも
可能である。The above-mentioned examples are for evaluating the lubricant, the lubrication method, and the bearing material for the high-speed rotating ball bearings.
This is done in order to realize and evaluate the slip that occurs in the actual ball bearing in a simpler model test, instead of rotating and evaluating the actual ball bearing. Therefore, it goes without saying that the materials of the rotating disk and the rotating ball, the lubrication method, and the lubricant can be changed according to the need for evaluation.
Further, it is also possible to carry out a test in an atmosphere other than the atmospheric atmosphere by sending an atmospheric gas such as an inert gas under pressure inside the cover.
【００４４】[0044]
【発明の効果】以上述べたように、本発明の摩擦摩耗試
験装置によれば、請求項１に示す構成により （１） 玉と軌道輪との転がり接触部形状を楕円形状に
模擬でき、その転がり接触部に生じる滑りの形態を、玉
軸受で実際に生じるものに近いものにできる。As described above, according to the frictional wear test apparatus of the present invention, the rolling contact portion between the ball and the bearing ring can be simulated to have an elliptical shape by the structure shown in claim 1. The form of slippage that occurs at the rolling contact can be close to what actually occurs in a ball bearing.
【００４５】また、請求項２に示す構成により、 （２） 公転滑りを発生させることができるばかりでな
く、実際の玉軸受で発生するスピン滑り速度を発生させ
ることができて、スピン滑りにより玉軸受に実際に生じ
る摩擦や摩耗を発生させることができる。According to the second aspect of the present invention, (2) not only the revolution slip can be generated, but also the spin slip velocity generated in the actual ball bearing can be generated, and the ball can be rotated by the spin slide. The friction and wear that actually occur in the bearing can be generated.
【００４６】また、請求項３に示す構成により、 （３） 高速玉軸受の有効な潤滑方法である、アンダー
レース潤滑法における、評価が困難であった、給油点か
ら軸受に至る油路における、油温や油量の効果を確認で
きる。According to the third aspect of the invention, (3) it is difficult to evaluate in the underrace lubrication method, which is an effective lubrication method for high-speed ball bearings, and in the oil passage from the oil supply point to the bearing, You can check the effect of oil temperature and oil amount.
【００４７】よって、本発明の摩擦摩耗試験装置によ
り、従来この種の摩擦摩耗試験装置に比べ、回転球と回
転平板の転がり接触部に発生する滑りを、実際の玉軸受
の玉と軌道みぞ間に生じる滑りに近づけ、玉軸受の構成
材料に関する耐摩耗性や耐焼き付き性、および潤滑剤の
潤滑特性や潤滑法の特質を評価するのに好適となる。Therefore, as compared with the conventional friction and wear test apparatus of this type, the friction and wear test apparatus of the present invention prevents the slip generated at the rolling contact portion between the rotating ball and the rotating flat plate from the ball of the actual ball bearing and the raceway groove. It is suitable for assessing the wear resistance and seizure resistance of the constituent materials of the ball bearing, and the lubrication characteristics of the lubricant and the characteristics of the lubrication method.
【００４８】さらに、高温使用限界付近の潤滑油による
流路の閉塞、遊離スラッジの転がり接触部への影響をも
評価できるようになる。Further, it becomes possible to evaluate the influence of the lubricating oil near the high temperature use limit on the blockage of the flow path and the influence of the loose sludge on the rolling contact portion.
【図１】本発明の第一実施例を示す主要部の断面図。FIG. 1 is a sectional view of a main part showing a first embodiment of the present invention.
【図２】本発明の第二実施例を示す主要部の断面図。FIG. 2 is a sectional view of a main part showing a second embodiment of the present invention.
【図３】本発明の第三実施例を示す主要部の断面図。FIG. 3 is a sectional view of a main part showing a third embodiment of the present invention.
【図４】本発明の第四実施例を示す主要部の断面図。FIG. 4 is a sectional view of a main portion showing a fourth embodiment of the present invention.
【図５】従来の、この種の摩擦摩耗試験装置の構成概念
図。FIG. 5 is a structural conceptual diagram of a conventional friction and wear test device of this type.
【図６】従来の、この種の摩擦摩耗試験装置の主要部の
断面図。FIG. 6 is a sectional view of a main part of a conventional friction and wear test device of this type.
【図７】玉軸受に発生する各種の滑りの説明図。FIG. 7 is an explanatory view of various slips that occur in the ball bearing.
【図８】玉軸受の転がり接触部の滑り、面圧、ＰＶ値、
摩耗形態の説明図。FIG. 8: Sliding of rolling contact portion of ball bearing, surface pressure, PV value,
Explanatory drawing of a worn form.
【図９】アンダーレース潤滑の例を示す断面図。FIG. 9 is a cross-sectional view showing an example of underlace lubrication.
１ 回転球 ２ 回転円板 ３、３′ 溝曲率部 ４ 回転軸 ５ 回転軸 ６ 凹所 ７ 潤滑油供給ノズル ８ 油溜まり ９ 油供給孔 １０ カバー DESCRIPTION OF SYMBOLS 1 rotating ball 2 rotating disk 3, 3'groove curvature part 4 rotating shaft 5 rotating shaft 6 recess 7 lubricating oil supply nozzle 8 oil sump 9 oil supply hole 10 cover
Claims (3)
負荷されて前記回転円板上を回動する回転球とにより玉
軸受の転がり接触部をモデル化し、前記接触部の材料、
潤滑剤、および潤滑方式による潤滑特性の評価を行うた
めの摩擦摩耗試験装置において、前記回転球の回動を、
前記回転円板の曲面部で行うようにしたことを特徴とす
る摩擦摩耗試験装置。1. A rolling contact part of a ball bearing is modeled by a rotating disk that rotates around an axis and a rotating ball that rotates on the rotating disk under a load, and a material of the contact part,
In the friction and wear test device for evaluating the lubrication characteristics by the lubricant and the lubrication method, the rotation of the rotating ball is
A frictional wear test device, characterized in that the test is performed on the curved surface portion of the rotating disk.
た溝曲率部であることを特徴とする請求項１の摩擦摩耗
試験装置。2. The friction and wear test apparatus according to claim 1, wherein the curved surface portion is a groove curvature portion that is recessed in the rotating disk.
ら供給される潤滑油を貯留する内部に画成された油溜ま
りと、前記回転円板に生じる遠心力により前記油溜まり
の潤滑油を前記曲面部に供給すべく、前記油溜まりと前
記曲面部の間に穿設された油供給孔を具えていることを
特徴とする請求項１、又は請求項２の摩擦摩耗試験装
置。3. An oil sump defined inside the rotating disk for storing lubricating oil supplied from an external lubricating oil supply system, and a centrifugal force generated on the rotating disk to lubricate the oil sump. The friction and wear test apparatus according to claim 1 or 2, further comprising an oil supply hole provided between the oil reservoir and the curved surface portion so as to supply oil to the curved surface portion.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17408794A JPH0835912A (en) | 1994-07-26 | 1994-07-26 | Frictional-wear testing apparatus |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17408794A JPH0835912A (en) | 1994-07-26 | 1994-07-26 | Frictional-wear testing apparatus |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0835912A true JPH0835912A (en) | 1996-02-06 |
Family
ID=15972431
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17408794A Pending JPH0835912A (en) | 1994-07-26 | 1994-07-26 | Frictional-wear testing apparatus |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0835912A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2011232156A (en) * | 2010-04-27 | 2011-11-17 | Mitsubishi Electric Corp | Wear test apparatus and wear test method |
| JP2013122442A (en) * | 2011-11-11 | 2013-06-20 | Kobe Steel Ltd | Method for testing rolling fatigue |
| CN105067468A (en) * | 2015-09-11 | 2015-11-18 | 姚钟钟 | Wear testing device |
| KR102122724B1 (en) * | 2019-05-09 | 2020-06-15 | (주)바이브록 | Galling phenomenon measuring device |
| CN112345228A (en) * | 2020-11-10 | 2021-02-09 | 长春理工大学 | Testing machine for detecting dynamic friction torque of turret seat ring |
-
1994
- 1994-07-26 JP JP17408794A patent/JPH0835912A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2011232156A (en) * | 2010-04-27 | 2011-11-17 | Mitsubishi Electric Corp | Wear test apparatus and wear test method |
| JP2013122442A (en) * | 2011-11-11 | 2013-06-20 | Kobe Steel Ltd | Method for testing rolling fatigue |
| CN105067468A (en) * | 2015-09-11 | 2015-11-18 | 姚钟钟 | Wear testing device |
| KR102122724B1 (en) * | 2019-05-09 | 2020-06-15 | (주)바이브록 | Galling phenomenon measuring device |
| CN112345228A (en) * | 2020-11-10 | 2021-02-09 | 长春理工大学 | Testing machine for detecting dynamic friction torque of turret seat ring |
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