JPH01259739A - Bearing device for electric rotary machine - Google Patents

Bearing device for electric rotary machine

Info

Publication number
JPH01259739A
JPH01259739A JP8415788A JP8415788A JPH01259739A JP H01259739 A JPH01259739 A JP H01259739A JP 8415788 A JP8415788 A JP 8415788A JP 8415788 A JP8415788 A JP 8415788A JP H01259739 A JPH01259739 A JP H01259739A
Authority
JP
Japan
Prior art keywords
bearing
outer ring
inner ring
rotor
shaft
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.)
Granted
Application number
JP8415788A
Other languages
Japanese (ja)
Other versions
JP2724154B2 (en
Inventor
Takashi Nagayama
孝 永山
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toshiba Corp
Original Assignee
Toshiba Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Toshiba Corp filed Critical Toshiba Corp
Priority to JP63084157A priority Critical patent/JP2724154B2/en
Publication of JPH01259739A publication Critical patent/JPH01259739A/en
Application granted granted Critical
Publication of JP2724154B2 publication Critical patent/JP2724154B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Abstract

PURPOSE:To decrease the relative rotational speed of the inner and outer rings of a bearing, by forming the outer ring of a first bearing fitting a rotor shaft to said inner shaft and the inner ring of a second bearing fitted to a frame supporting a stator into an integral body. CONSTITUTION:A rotating shaft 4 fitted to the rotor 3 of an electric rotary machine is fitted to the inner ring of a first bearing 5. Also, a frame 1 is provided with a second bearing 8, the outer ring of said bearing 8 is fastened to said frame 1, and the inner ring 10 of said bearing 8 is formed into an integral body with the outer ring 10 of said bearing 5. Said bearings 5 and 8 are juxtaposed in the axial direction and the diameter of the inner ring of said bearing 8 is made smaller than that of the outer ring of said bearing 5. Thus, the number of relative revolutions of the inner and outer rings of a bearing is made small and the rotational speed is increased without impairing lubricating properties.

Description

【発明の詳細な説明】 [発明の目的] (産業上の利用分野) 本発明は車輌用の回転電機の軸受装置に係り、さらに詳
細には、シャフトのより高速回転を可能にする軸受装置
に関する。
[Detailed Description of the Invention] [Object of the Invention] (Industrial Field of Application) The present invention relates to a bearing device for a rotating electric machine for a vehicle, and more particularly, to a bearing device that enables a shaft to rotate at a higher speed. .

(従来の技術) 従来の車輌用の回転電機は、概略的には、第7図に示す
ごとき構造である。第7図は、回転電機のシャフトを通
る平面で断面にしたもので、図中の符号1は回転電機の
フレームでその内側に一次コイル(図示省略)を巻回し
た固定子2が装着されている。また、符@3は二次コイ
ル(図示省略)を巻回した回転子でシャフト4に嵌合固
定されている。
(Prior Art) A conventional rotating electric machine for a vehicle has a structure as schematically shown in FIG. 7. Fig. 7 is a cross section taken along a plane passing through the shaft of a rotating electric machine. Reference numeral 1 in the figure is the frame of the rotating electric machine, and a stator 2 with a primary coil (not shown) wound inside the frame is attached. There is. Further, the symbol @3 denotes a rotor around which a secondary coil (not shown) is wound, and is fitted and fixed to the shaft 4.

上記シャフト4は、軸受5.6を介してフレーム1に回
転可能に支承されており、とのシャフト4の一端部は、
歯車装量(図示省略)を介して車輌の車輪を駆動するた
めに、カップリング7を介して歯車@置に連動連結して
あり、回転電機の駆動力を車輪に伝達している。前記軸
受5.6は、−殻内なものであって、内輪と外輪との間
に多数のローラー又はボールをリティナー(保持器)を
介して配設保持した構成である。
The shaft 4 is rotatably supported by the frame 1 via a bearing 5.6, and one end of the shaft 4 is
In order to drive the wheels of the vehicle through a gear arrangement (not shown), it is interlocked with a gear arrangement via a coupling 7, and transmits the driving force of the rotating electric machine to the wheels. The bearing 5.6 is an in-shell type, and has a structure in which a large number of rollers or balls are arranged and held between an inner ring and an outer ring via a retainer.

ところで、車輌独自の制約として、回転電機の構成スペ
ースが非常に小さいこと、又、回転電機の性能をいつま
でも良好に保つために定期的に行うメインテナンスを容
易に行なうことができることなどから、軸受5の潤滑方
式としては、その性能の割には構造が簡単でコンパクト
に構成できるグリース潤滑が非常に一般的である。
By the way, there are constraints unique to vehicles, such as the fact that the space for the rotating electric machine is extremely small, and the fact that periodic maintenance can be easily performed to keep the rotating electric machine in good condition. Grease lubrication is a very common lubrication method because it has a simple and compact structure considering its performance.

また、近年においては、車輌の性能向上の一環として起
動加速度のアップと、車輌の軽量化が非常に強く要望さ
れている。その対策の一つとして、歯車装置の歯数比を
上げて回転電機を高速回転で使用する方法がある。回転
電機を高速で回転させることにより、回転電標の小さな
トルクで今まで以上の車輌性能つまり起動加速度を向上
させることができることになる。又回転電機のトルクが
小さくなった分だけ、回転電機の小形軽量化を図ること
ができる。ところが、前述したように、回転電機は軸受
5.6を介してシャフト4を支承し、シャフト4に固定
した回転子3を回して駆動力を発生させるので、回転子
3の回転数を上げると、車輌性能の向上とは逆に、次の
ような問題が軸受5.6に発生する。
Furthermore, in recent years, as part of efforts to improve vehicle performance, there has been a strong desire to increase starting acceleration and to reduce the weight of vehicles. One of the countermeasures is to use the rotating electric machine at high speed by increasing the gear ratio of the gears. By rotating the rotating electric machine at high speed, it is possible to improve the vehicle performance, that is, the starting acceleration, with a small torque from the rotating electric sign. Furthermore, since the torque of the rotating electrical machine is reduced, the rotating electrical machine can be made smaller and lighter. However, as mentioned above, the rotating electric machine supports the shaft 4 via the bearings 5 and 6 and rotates the rotor 3 fixed to the shaft 4 to generate driving force, so if the rotation speed of the rotor 3 is increased, However, contrary to the improvement in vehicle performance, the following problems occur in the bearing 5.6.

すなわち、軸受5.6の潤滑性能の低下である。That is, the lubrication performance of the bearing 5.6 is reduced.

一般に、軸受部には、軸受の大きさと回転数を乗じた数
に比例して潤滑性能が低下する現象がある。
Generally, there is a phenomenon in bearings in which the lubrication performance decreases in proportion to the product of the size of the bearing and the number of rotations.

この低下する度合は潤滑用語のdmN値で評価される。The degree of this decrease is evaluated by the dmN value, which is a lubricant term.

すなわち、ころがり軸受の場合、dmとは第8図に図示
されるように、軸受5の外輪5aの外径りと内輪5bの
内径dの平均値であり、Nとはこの軸受の外輪5aと内
輪5bの相対的な回転数である。したがって、外輪5a
が回転しないで固定されていれば内輪5bの回転数であ
る。
That is, in the case of a rolling bearing, dm is the average value of the outer diameter of the outer ring 5a and the inner diameter d of the inner ring 5b of the bearing 5, as shown in FIG. This is the relative rotation speed of the inner ring 5b. Therefore, the outer ring 5a
If it is fixed without rotating, it is the rotation speed of the inner ring 5b.

最近のめざましい潤滑油の性能アップにより潤滑性能に
支障を来たさない許容dmN値は徐々に高くなってきて
いる。しかし車輌の性能の向上、換言すれば回転電機の
高速化はそれ以上に技術的進歩が早く、回転電機の高速
化はdmN値対策であると言うことも可能である。
Due to the recent remarkable improvement in the performance of lubricating oils, the permissible dmN value that does not impede lubrication performance is gradually increasing. However, technological progress has been faster in improving the performance of vehicles, in other words, increasing the speed of rotating electric machines, and it can be said that increasing the speed of rotating electric machines is a measure against the dmN value.

(発明が解決しようとする課題) 前述したように、従来においての回転電機の高速化は、
dIllN値上潤滑性が低下し、軸受の焼付などが発生
する問題があり、回転電機のより高速化が困難であると
いう問題があった。また軸受の寸法を可能な限り小さく
することによりdmN値を下げることができる。しかし
、シャフトの剛性や強度上から現在はほとんど限界設計
に近ずいており、回転電機のより高速化が非常に困難視
されていた。
(Problem to be solved by the invention) As mentioned above, increasing the speed of conventional rotating electric machines
There is a problem in that the dIllN value lowers the lubricity and seizure of the bearing occurs, and it is difficult to increase the speed of the rotating electric machine. Furthermore, the dmN value can be lowered by making the dimensions of the bearing as small as possible. However, due to the rigidity and strength of the shaft, the design is currently close to its limit, making it extremely difficult to increase the speed of rotating electric machines.

本発明は上記のごとき問題に鑑みてなされたもので、軸
受のdmN値は従来程度を保持しつつも、回転電機にお
いて従来以上の高速化を可能にした軸受装置を提供しよ
うとするものである。
The present invention has been made in view of the above-mentioned problems, and aims to provide a bearing device that maintains the dmN value of the bearing at the same level as conventional bearings, while enabling higher speeds in rotating electric machines than conventional ones. .

[発明の構成] (課題を解決するための手段) 前述の課題を解決するために、本発明においては、回転
電機における固定子を支障したフレームに、回転子を取
付けたシャフトを回転自在に支承する軸受装置において
、前記シャフトに内輪を嵌合した第一の軸受の外輪と前
記フレームに外輪を支障された第二の軸受の内輪とを一
体的に設けてなり、第一の軸受の外輪と第二の軸受の内
輪とを中間体を介して一体化してなるものである。
[Structure of the Invention] (Means for Solving the Problems) In order to solve the above-mentioned problems, in the present invention, a shaft on which a rotor is attached is rotatably supported in a frame that obstructs a stator in a rotating electric machine. In the bearing device, an outer ring of a first bearing whose inner ring is fitted to the shaft and an inner ring of a second bearing whose outer ring is blocked by the frame are integrally provided, and the outer ring of the first bearing and the inner ring of the second bearing are integrally provided. It is formed by integrating the inner ring of the second bearing via an intermediate body.

(作用) 上記構成において、回転電機のシャフトを回転すると、
第一の軸受の内輪はシャフトと一体となって回転し、外
輪は、内輪と外輪との間に配置された複数のローラまた
はボールとのころがり摩擦により、内輪と同方向へ低速
回転することとなる。すなわち、回転電機の回転子の回
転を複数の軸受で分担することとなり、軸受の回転数を
例えば1/2と小さくすることができる。また軸受全体
として見た場合、静止状態にある外輪の外径を小さくで
きるので、軸受のdmN値を上げずに回転電機の高速化
を図ることができるものである。
(Function) In the above configuration, when the shaft of the rotating electric machine is rotated,
The inner ring of the first bearing rotates together with the shaft, and the outer ring rotates at low speed in the same direction as the inner ring due to rolling friction with a plurality of rollers or balls arranged between the inner ring and the outer ring. Become. In other words, the rotation of the rotor of the rotating electric machine is shared by a plurality of bearings, and the rotation speed of the bearings can be reduced to, for example, 1/2. Furthermore, when looking at the bearing as a whole, since the outer diameter of the outer ring in a stationary state can be reduced, the speed of the rotating electric machine can be increased without increasing the dmN value of the bearing.

(実施例) 以下、図面を用いて本発明の実施例について詳細に説明
する。なお、前記第7図に示した従来の構成と重複する
構成部分には同一符号を付することとして、詳細な説明
は省略する。
(Example) Hereinafter, an example of the present invention will be described in detail using the drawings. Components that overlap with the conventional configuration shown in FIG. 7 are designated by the same reference numerals and detailed explanations will be omitted.

第1図を参照するに、第一の軸受5の内輪はシャフト4
に嵌合固定されており、この軸受5の外輪とフレーム1
の間には、第二の軸受8が設けである。この第二の軸受
8の外輪はフレーム1に支承されており、内輪は第一の
軸受5の外輪と筒状の中間体10を介して一体的に連結
されている。
Referring to FIG. 1, the inner ring of the first bearing 5 is connected to the shaft 4.
The outer ring of the bearing 5 and the frame 1
A second bearing 8 is provided between them. The outer ring of the second bearing 8 is supported by the frame 1, and the inner ring is integrally connected to the outer ring of the first bearing 5 via a cylindrical intermediate body 10.

第1図より明らかなように、第一の軸受5と第二の軸受
8は、シャフト4の軸方向に並設してあり、第一の軸受
5の外輪の径よりも第二の軸受8の内輪の径を小さく設
けである。したがって、この構成によれば、軸受部の全
体的な構成として見ると、静止状態にある外輪の外径を
小さくでき、前記dmを小さくすることができる。
As is clear from FIG. 1, the first bearing 5 and the second bearing 8 are arranged in parallel in the axial direction of the shaft 4, and the diameter of the outer ring of the first bearing 5 is larger than that of the second bearing 8. The diameter of the inner ring is made smaller. Therefore, according to this configuration, when viewed from the overall configuration of the bearing portion, the outer diameter of the outer ring in a stationary state can be reduced, and the above-mentioned dm can be reduced.

前記中間体10は、大径部10Lと小径部10Sとを備
えた筒状をなしており、この中間体10の大径部10L
内に第一の軸受5の外輪が嵌入してあり、中間体10の
小径部10Sは、第二の軸受8の内輪の内側に嵌入しで
ある。なお、シャフト4の細端部を支障した軸受6は、
第7図に示した従来の構造と全く同一の構造である。
The intermediate body 10 has a cylindrical shape including a large diameter portion 10L and a small diameter portion 10S.
The outer ring of the first bearing 5 is fitted inside, and the small diameter portion 10S of the intermediate body 10 is fitted inside the inner ring of the second bearing 8. In addition, the bearing 6 that interfered with the narrow end of the shaft 4 is
This structure is exactly the same as the conventional structure shown in FIG.

上記構成において、中間体10を備えた軸受の構成では
回転電機の回転子3、シャフト4の回転を第一の軸受5
および第二の軸受8で分担して受けもつので、各軸受の
回転数はほぼ半分となる。
In the above configuration, in the configuration of the bearing including the intermediate body 10, the rotation of the rotor 3 and shaft 4 of the rotating electric machine is transferred to the first bearing 5.
Since the second bearing 8 shares the responsibility, the number of rotations of each bearing is approximately halved.

したがって、軸受5および軸受8のdmN値上許容でき
る回転数を倍にすることができ、回転電機の回転子3の
回転数を従来の倍に高速化することができることとなる
Therefore, the permissible rotational speed of the bearings 5 and 8 based on the dmN value can be doubled, and the rotational speed of the rotor 3 of the rotating electric machine can be increased to twice the conventional speed.

第2図は、中間体10の方向性を逆にして、第1図にお
ける第一の軸受5と第二の軸受8の軸方向の配置関係を
逆にしたもので、効果は第1図に示した実施例と全く同
様の効果を奏する。
In FIG. 2, the directionality of the intermediate body 10 is reversed, and the axial arrangement relationship of the first bearing 5 and the second bearing 8 in FIG. 1 is reversed, and the effect is the same as in FIG. The effect is exactly the same as that of the embodiment shown.

第3図はシャフト4の両端部側を共に複数の軸受5.8
および軸受6.9でもって支承した2段軸受構造にした
もので、第1図、第2図に示した実施例の場合に比較し
て、両端部側とも2段軸受構造であるので、より高速化
が可能なものである。
Figure 3 shows a plurality of bearings 5.8 on both ends of the shaft 4.
It has a two-stage bearing structure supported by a bearing 6.9, and compared to the embodiment shown in Figs. 1 and 2, it has a two-stage bearing structure on both end sides, so It is possible to increase the speed.

第4図〜第6図は前記中間体10と回転子3との間に、
回転を制御できる回転調整装置11を設けた態様を示す
ものである。
4 to 6 show that between the intermediate body 10 and the rotor 3,
This shows an embodiment in which a rotation adjustment device 11 that can control rotation is provided.

すなわち、第4図においては、回転調整装置11として
、中間体10にN、Sの磁極をもつ永久磁石12を、中
間体10の円周方向に交互に設け、この磁石12に対向
する位置の回転子3に、うず電流を発生しやすい例えば
アルミ板のようなドーナツ状の円板13を設けて構成し
たものである。
That is, in FIG. 4, as the rotation adjustment device 11, permanent magnets 12 having N and S magnetic poles are provided alternately in the circumferential direction of the intermediate body 10, and permanent magnets 12 having N and S magnetic poles are provided at positions opposite to the magnets 12. The rotor 3 is provided with a donut-shaped disk 13, such as an aluminum plate, which tends to generate eddy current.

したがって、この構成において、中間体10は磁石12
を介して、すべりを発生しながらも回転子3の回転方向
に回転を促進させられつつ回転するこことなる。
Therefore, in this configuration, the intermediate body 10 is the magnet 12
Through this, the rotor 3 rotates while being accelerated in the rotational direction of the rotor 3, even though slippage occurs.

第5図は回転子3に風穴14を設けると共に回転子3の
側部に送」ファン15を設け、かつ中間体10に受風フ
ァン16を設けた構成を示すものである。
FIG. 5 shows a configuration in which the rotor 3 is provided with air holes 14, a blower fan 15 is provided on the side of the rotor 3, and a blower fan 16 is provided on the intermediate body 10.

この構成によれば、回転子3の回転により、送風ファン
15によって発生する風が受風ファン16に送風され、
中間体10の回転が促進されるものである。
According to this configuration, the rotation of the rotor 3 causes the wind generated by the blower fan 15 to be blown to the blower fan 16,
The rotation of the intermediate body 10 is promoted.

第6図は中間体10の回転力を抑制するために、中間体
10の外周面に複数のフィン17を突設してなるもので
ある。
In FIG. 6, a plurality of fins 17 are provided protruding from the outer peripheral surface of the intermediate body 10 in order to suppress the rotational force of the intermediate body 10.

この構成によれば、突出したフィン17が回転力にブレ
ーキをかけることとなり、回転力を抑制する効果を秦す
るものである。
According to this configuration, the protruding fins 17 apply a brake to the rotational force, thereby reducing the effect of suppressing the rotational force.

なお、本発明は前述の実施例のみに限るものではなく、
例えば軸受を三重構造以上とすることも可能であり、種
々の変更を行なうことにより、その他の態様でも実施可
能である。
Note that the present invention is not limited to the above-mentioned embodiments.
For example, it is possible to make the bearing have a triple or more structure, and by making various changes, other embodiments are also possible.

[発明の効果] 以上のごとき実施例の説明より理解されるように、本発
明によれば、軸受における内輪と外輪との間の相対的な
回転数を小さくできる。したがって、6mN値を従来程
度に保持して、軸受の潤滑性をそこなうことなく、回転
電機のより高速化を図ることができる。
[Effects of the Invention] As can be understood from the description of the embodiments above, according to the present invention, the relative rotational speed between the inner ring and the outer ring in the bearing can be reduced. Therefore, it is possible to maintain the 6 mN value at the conventional level and increase the speed of the rotating electrical machine without impairing the lubricity of the bearing.

【図面の簡単な説明】[Brief explanation of the drawing]

図面は本発明の実施例を示すもので、第1図は本発明の
一実施例を示す断面図である。 第2図は他の実施例を示す断面図で、第1図の軸受の順
序を逆にしたものである。 第3図はシャフトの両端部の軸受を2段にした実施例を
示す断面図である。 第4図および第5図は軸受装置における中間体と回転子
との間に、中間体の回転を促進させる回転調整装置を設
けた実施例を示す主要部の断面図である。 第6図は中間体の回転を抑制させる回転[!装置を設け
た実施例を示す主要部の断面図である。 第7図は従来の車輌用の回転電機の一般的な構造を示す
概略的な縦断組立図である。 第8図はローラー軸受の回転軸を通る平面で縦断した図
で、ころがり軸受の一例を示すものである。 1・・・フレーム 2・・・固定子 3・・・回転子 4・・・シャフト 5・・・軸受 5a・・・外輪 5b・・・内輪 8・・・軸受 10・・・中間体 11・・・回転調整装置
The drawings show an embodiment of the present invention, and FIG. 1 is a sectional view showing one embodiment of the present invention. FIG. 2 is a sectional view showing another embodiment, in which the order of the bearings in FIG. 1 is reversed. FIG. 3 is a sectional view showing an embodiment in which the bearings at both ends of the shaft are arranged in two stages. FIGS. 4 and 5 are cross-sectional views of main parts showing an embodiment in which a rotation adjusting device for promoting rotation of the intermediate body is provided between the intermediate body and the rotor in the bearing device. Figure 6 shows the rotation [!] that suppresses the rotation of the intermediate body. FIG. 2 is a cross-sectional view of the main parts of an embodiment in which the device is provided. FIG. 7 is a schematic vertical assembly diagram showing the general structure of a conventional rotating electric machine for a vehicle. FIG. 8 is a longitudinal sectional view taken along a plane passing through the rotation axis of the roller bearing, and shows an example of a rolling bearing. 1... Frame 2... Stator 3... Rotor 4... Shaft 5... Bearing 5a... Outer ring 5b... Inner ring 8... Bearing 10... Intermediate body 11.・Rotation adjustment device

Claims (2)

【特許請求の範囲】[Claims] (1)回転電機における固定子を支承したフレームに、
回転子を取付けたシャフトを回転自在に支承する軸受装
置において、前記シャフトに内輪を嵌合した第一の軸受
の外輪と前記フレームに外輪を支承された第二の軸受の
内輪とを一体的に設けてなり、第一の軸受の外輪と第二
の軸受の内輪とを中間体を介して一体化してなることを
特徴とする回転電機の軸受装置。
(1) In the frame that supports the stator of the rotating electric machine,
In a bearing device that rotatably supports a shaft to which a rotor is attached, an outer ring of a first bearing whose inner ring is fitted to the shaft and an inner ring of a second bearing whose outer ring is supported by the frame are integrated. 1. A bearing device for a rotating electrical machine, characterized in that the outer ring of the first bearing and the inner ring of the second bearing are integrated via an intermediate.
(2)中間体と回転子との間に、回転子の回転に応じて
中間体の回転を調整可能な回転調整装置を設けてなるこ
とを特徴とする請求項1記載の回転電機の軸受装置。
(2) A bearing device for a rotating electric machine according to claim 1, characterized in that a rotation adjustment device is provided between the intermediate body and the rotor, which can adjust the rotation of the intermediate body according to the rotation of the rotor. .
JP63084157A 1988-04-07 1988-04-07 Bearing device for rotating electric machine Expired - Lifetime JP2724154B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP63084157A JP2724154B2 (en) 1988-04-07 1988-04-07 Bearing device for rotating electric machine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP63084157A JP2724154B2 (en) 1988-04-07 1988-04-07 Bearing device for rotating electric machine

Publications (2)

Publication Number Publication Date
JPH01259739A true JPH01259739A (en) 1989-10-17
JP2724154B2 JP2724154B2 (en) 1998-03-09

Family

ID=13822667

Family Applications (1)

Application Number Title Priority Date Filing Date
JP63084157A Expired - Lifetime JP2724154B2 (en) 1988-04-07 1988-04-07 Bearing device for rotating electric machine

Country Status (1)

Country Link
JP (1) JP2724154B2 (en)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS53113947A (en) * 1977-03-14 1978-10-04 Maschf Augsburg Nuernberg Ag Bearing for supercritical lotation rotor

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS53113947A (en) * 1977-03-14 1978-10-04 Maschf Augsburg Nuernberg Ag Bearing for supercritical lotation rotor

Also Published As

Publication number Publication date
JP2724154B2 (en) 1998-03-09

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