JPH088756B2 - AC generator with vacuum pump - Google Patents
AC generator with vacuum pumpInfo
- Publication number
- JPH088756B2 JPH088756B2 JP3230774A JP23077491A JPH088756B2 JP H088756 B2 JPH088756 B2 JP H088756B2 JP 3230774 A JP3230774 A JP 3230774A JP 23077491 A JP23077491 A JP 23077491A JP H088756 B2 JPH088756 B2 JP H088756B2
- Authority
- JP
- Japan
- Prior art keywords
- rotor
- vacuum pump
- generator
- shaft
- 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.)
- Expired - Fee Related
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- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
- Motor Or Generator Frames (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は、車両用内燃機関の補機
である真空ポンプ付の発電機に係り、特に自動車用ディ
ーゼルエンジンに装備するのに好適な真空ポンプ付交流
発電機に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a generator equipped with a vacuum pump, which is an auxiliary machine of an internal combustion engine for a vehicle, and more particularly to an AC generator equipped with a vacuum pump suitable for mounting on a diesel engine for automobiles.
【０００２】[0002]
【従来の技術】従来から、自動車など車両では、ブレー
キ倍力装置など真空をエネルギー源とした各種の機器が
使用されているが、このとき、ガソリンエンジンでは、
このエネルギー源となる真空源として、エンジンの吸気
負圧を利用するのが一般的であった。2. Description of the Related Art Conventionally, in a vehicle such as an automobile, various devices such as a brake booster using a vacuum as an energy source have been used.
It is common to use the intake negative pressure of the engine as a vacuum source that serves as this energy source.
【０００３】然し乍ら、ディーゼルエンジンの自動車で
は、エンジンの吸気負圧が充分に得られないので、この
ときには、別途、真空ポンプの装備を要する。そこで、
エンジン補機として、ほとんど欠かせない装備品である
発電機に真空ポンプを組合せた、真空ポンプ付交流発電
機が従来から知られており、その例を特公昭６３−８９
０３４号公報などに見ることができる。However, since a diesel engine automobile cannot obtain a sufficient intake negative pressure of the engine, a vacuum pump is additionally required at this time. Therefore,
As an engine auxiliary machine, an AC generator with a vacuum pump, which combines a vacuum pump with a generator, which is almost indispensable equipment, has been known in the past, and an example thereof is JP-B-63-89.
It can be found in Japanese Patent Publication No. 034.
【０００４】そして、この従来技術では、両軸両軸受形
の発電機の回転子の一方の軸受の外側の軸端に、偏心形
ベーンポンプからなる真空ポンプのロータを取付け、こ
のロータが発電機の回転界磁形回転子と一緒にエンジン
で駆動されるようにし、必要とする真空を発生するよう
になっているのであるが、このとき、真空ポンプの中で
回転するロータに設けられているベーンの枚数ｎに比例
して回転ｎ次振動が発生する。In this prior art, a rotor of a vacuum pump consisting of an eccentric vane pump is attached to the outer shaft end of one bearing of a rotor of a double-shaft double-bearing type generator, and this rotor serves as a generator. It is designed to generate the required vacuum by being driven by the engine together with the rotating field type rotor. At this time, the vanes provided on the rotor rotating in the vacuum pump are used. Rotational nth order vibration is generated in proportion to the number n of sheets.
【０００５】[0005]
【発明が解決しようとする課題】上記従来技術は、発電
機回転子軸受間の距離、発電機回転子軸の剛性、回転子
質量の関係から決まる回転子の固有振動数ｆo が、機関
の実用回転域において、真空ポンプにより発生する回転
ｎ次振動数より低い領域になってしまう点について配慮
がされておらず、実用回転速度領域内の高回転域で、回
転子固有振動数と真空ポンプを加振源とする回転ｎ次振
動数が一致して共振現象が発生し、この結果、回転子軸
が振られて回転子軸に固定されているスリップリングの
摺動面が振れ、スリップリングとブラシの接触が不安定
になり、発電機の出力電流のふらつきや出力電流の低
下、さらには摺動面荒れによるブラシやスリップリング
の早期摩耗が発生するという問題があった。In the above-mentioned prior art, the natural frequency fo of the rotor determined by the relationship between the distance between the generator rotor bearings, the rigidity of the generator rotor shaft, and the rotor mass is the practical frequency of the engine. In the rotation range, no consideration is given to the range lower than the nth order rotation frequency generated by the vacuum pump, and the rotor natural frequency and the vacuum pump are set in the high rotation range within the practical rotation speed range. A resonance phenomenon occurs when the n-th rotation frequency of the vibration source coincides with each other, and as a result, the rotor shaft vibrates and the sliding surface of the slip ring fixed to the rotor shaft vibrates, and There is a problem that the contact of the brush becomes unstable, the output current of the generator fluctuates, the output current decreases, and the brush and the slip ring are prematurely worn due to the roughening of the sliding surface.
【０００６】本発明の目的は、実用回転速度領域におい
て、真空ポンプを加振源とする回転ｎ次振動数と発電機
回転子固有振動数が一致する虞れがなく、常に安定した
発電機出力が得られるようにした真空ポンプ付交流発電
機を提供することにある。It is an object of the present invention that, in the practical rotation speed range, there is no possibility that the n-th frequency of rotation using the vacuum pump as the vibration source and the natural frequency of the generator rotor will match, and the generator output will always be stable. Another object of the present invention is to provide an alternating current generator with a vacuum pump that can achieve the above.
【０００７】[0007]
【課題を解決するための手段】上記目的は、回転子の質
量をｍ〔Ｋｇ〕、回転子の回転軸のヤング率をＥ〔Ｎ／
ｍｍ 2 〕、平均軸径をｄ〔ｍｍ〕、回転子の中心から一
方の軸受の中心までの軸の長さをＬ1〔ｍｍ〕、回転子
の中心から他方の軸受の中心までの軸の長さをＬ2〔ｍ
ｍ〕、真空ポンプのベーンの個数をｎ、そして回転子の
最高回転速度をＮ〔ｒｐｍ〕としたとき、The above-mentioned objects are as follows: the mass of the rotor is m [ Kg ], and the Young's modulus of the rotating shaft of the rotor is E [ N /
mm 2 ], the average shaft diameter is d [mm], the length of the shaft from the center of the rotor to the center of one bearing is L 1 [mm], and the length of the shaft from the center of the rotor to the center of the other bearing is Length is L 2 [m
m], the number of vanes of the vacuum pump is n, and the maximum rotation speed of the rotor is N [rpm],
【０００８】[0008]
【数１】 [Equation 1]
【０００９】の関係が成立するように、各部を構成する
ことにより達成される。This is achieved by configuring each part so that the relationship of [1] is established.
【００１０】[0010]
【作用】回転子の固有振動数ｆo〔Ｈｚ〕は、次の(1)式
で与えられる。The natural frequency fo [Hz] of the rotor is given by the following equation (1).
【００１１】[0011]
【数２】 [Equation 2]
【００１２】一方、真空ポンプを加振源とする回転ｎ次
振動数ｆn〔Ｈｚ〕は、次の(2)式で与えられる。On the other hand, the rotational n-th order frequency fn [Hz] using a vacuum pump as an excitation source is given by the following equation (2).
【００１３】[0013]
【数３】 (Equation 3)
【００１４】従って、ｆo ＞ｆn の関係が満足されるよ
うに、すなわち、次の式が成立するように構成してやれ
ば、どのような運転状態になっても共振現象発生の虞れ
は無くなり、常に安定した発電電力の供給を得ることが
できる。Therefore, if the construction is made so that the relation fo> fn is satisfied, that is, the following equation is established, the fear of occurrence of the resonance phenomenon disappears under any operating condition, and it is always possible. It is possible to obtain a stable supply of generated power.
【００１５】[0015]
【数１】 [Equation 1]
【００１６】[0016]
【実施例】以下、本発明による真空ポンプ付交流発電機
について、図示の実施例により詳細に説明する。図２
は、本発明の一実施例で、図において、ＡＣＧが交流発
電機を、そしてＶＰが真空ポンプを表わし、１は回転
子、１ａは回転子軸、１ｂはセレーション、２は界磁コ
イル、３ａ、３ｂはスリップリング、３ｃはフロントカ
バー、３ｄはリヤカバー、４ａはブラシ保持器、４ｂ、
４ｃはブラシ、５は整流装置、６はプーリ、７、８は軸
受、９は固定子鉄心、９ａは３相巻線からなる電機子コ
イル、１０、１０ａはボルト、１１は真空ポンプＶＰの
ロータ、１２は真空ポンプＶＰのケーシング、１３は真
空ポンプＶＰのベーンである。EXAMPLES An AC generator with a vacuum pump according to the present invention will be described in detail below with reference to the illustrated examples. Figure 2
Is an embodiment of the present invention, in which ACG represents an alternator and VP represents a vacuum pump, 1 is a rotor, 1a is a rotor shaft, 1b is serration, 2 is a field coil, 3a. 3b is a slip ring, 3c is a front cover, 3d is a rear cover, 4a is a brush holder, 4b,
4c is a brush, 5 is a rectifying device, 6 is a pulley, 7 and 8 are bearings, 9 is a stator core, 9a is an armature coil consisting of three-phase windings, 10 and 10a are bolts, and 11 is a rotor of the vacuum pump VP. , 12 are casings of the vacuum pump VP, and 13 are vanes of the vacuum pump VP.
【００１７】回転子１は、図１に詳細に示されているよ
うに、極の形状が爪形のポールコアと、円筒状の界磁コ
イル２を備え、この界磁コイル２は、回転子軸１ａに同
軸的に嵌合されたモールド成形品に圧入した金属環から
なる、２個のスリップリング３ａ、３ｂに接続されてい
る。一方、これらスリップリング３ａ、３ｂには、ブラ
シ保持器４ａ内に保持されて軸方向に並んで配置されて
いるブラシ４ｂ、４ｃがそれぞれ摺動接触し、整流装置
５を介して電機子コイル９ａから供給される直流電流が
界磁コイル２に供給されるようにし、これにより回転子
１が励磁されるようになっている。As shown in detail in FIG. 1, the rotor 1 includes a pole core having a claw-shaped pole and a cylindrical field coil 2. The field coil 2 has a rotor shaft. It is connected to two slip rings 3a and 3b made of a metal ring press-fitted into a molded product coaxially fitted to 1a. On the other hand, the brushes 4b and 4c, which are held in the brush holder 4a and arranged side by side in the axial direction, are in sliding contact with the slip rings 3a and 3b, respectively, and the armature coil 9a is mediated by the rectifier 5. The DC current supplied from the field coil 2 is supplied to the field coil 2, whereby the rotor 1 is excited.
【００１８】回転子軸１ａの両側は、それぞれフロント
カバー３ｃとリヤカバー３ｄに設けられている軸受７、
８により軸支されており、フロントカバー３ｃから突き
出た軸端にはプーリ６が取付られている。フロントカバ
ー３ｃとリヤカバー３ｄは、それぞれ３相の電機子コイ
ル９ａが巻装された固定子鉄心９の外周両端面に当接嵌
合され、ボルト１０により固定されている。Bearings 7 are provided on the front cover 3c and the rear cover 3d on both sides of the rotor shaft 1a, respectively.
8 is pivotally supported, and a pulley 6 is attached to the shaft end protruding from the front cover 3c. The front cover 3c and the rear cover 3d are abutted and fitted to both outer peripheral end faces of the stator core 9 around which the three-phase armature coils 9a are wound, and are fixed by bolts 10.
【００１９】そこで、図示してない、ディーゼルエンジ
ンなど、外部の駆動装置からベルトを介してプーリ６が
回転駆動されると、回転子１が回転駆動され、発電動作
が得られることになる。そして、この実施例では、回転
軸１ａに与えられる最高回転速度Ｎが１１５００〔ｒｐ
ｍ〕になるように、駆動側と非駆動側のプーリ比が選ば
れている。Therefore, when the pulley 6 is rotationally driven by an external driving device (not shown) such as a diesel engine via the belt, the rotor 1 is rotationally driven and a power generating operation is obtained. In this embodiment, the maximum rotation speed N given to the rotary shaft 1a is 11500 [rp
m], the drive-side and non-drive-side pulley ratios are selected.
【００２０】次に、回転軸１ａのプーリ６が設けられて
いる軸端とは反対側の軸端にはセレーション１ｂが設け
られており、これに真空ポンプＶＰのロータ１１が嵌合
されている。この真空ポンプＶＰは偏心形ベーンポンプ
と呼ばれるタイプのものであり、従って、ロータ１１に
は、径方向に開口している４個の溝が、ロータ１１の周
方向に等間隔で設けられており、これらの溝には、それ
ぞれロータ１１の径方向へ摺動運動が可能な４個のベー
ン１３が挿嵌されている。Next, a serration 1b is provided at the shaft end of the rotary shaft 1a opposite to the shaft end at which the pulley 6 is provided, and the rotor 11 of the vacuum pump VP is fitted therein. . This vacuum pump VP is of a type called an eccentric vane pump. Therefore, the rotor 11 is provided with four radially open grooves, which are arranged at equal intervals in the circumferential direction of the rotor 11. Four vanes 13 that can slide in the radial direction of the rotor 11 are fitted into these grooves.
【００２１】そして、このロータ１１はケーシング１２
の円筒状をなしている内側空間部内に、偏心した状態で
保持され、この内側空間部の内周面に、４個のベーン１
３の外側端部が、図示してないスプリングの力と遠心力
により、当接押圧された状態で摺動回転されるようにな
っている。また、このケーシング１２は、交流発電機Ａ
ＣＧのリヤカバー３ｄの背面にボルト１０ａによって固
定されている。そこで、交流発電機ＡＣＧの回転子１が
回転駆動されると、真空ポンプＶＰのロータ１１も一緒
に回転し、周知の偏心形ベーンポンプとして動作し、真
空が得られることになる。The rotor 11 has a casing 12
Is held in an eccentric state in the inner space portion having a cylindrical shape, and four vanes 1 are provided on the inner peripheral surface of the inner space portion.
The outer end portion of 3 is slidably rotated by a force of a spring (not shown) and a centrifugal force in a contact and pressed state. In addition, this casing 12 is an AC generator A.
It is fixed to the back surface of the rear cover 3d of the CG by bolts 10a. Therefore, when the rotor 1 of the AC generator ACG is rotationally driven, the rotor 11 of the vacuum pump VP also rotates and operates as a well-known eccentric vane pump to obtain a vacuum.
【００２２】ところで、以上のようにして、交流発電機
ＡＣＧと真空ポンプＶＰが回転駆動されると、真空ポン
プＶＰを加振源とする回転ｎ次の振動が、図３に示すよ
うに発生する。ここで、ｎはベーン１３の個数であり、
従って、この実施例では、上記したように、ｎ＝４であ
る。そこで、いま、実用最高回転数Ｎ〔ｒｐｍ〕とする
と、この場合には、その振動数は０〔Ｈｚ〕〜ｎ・Ｎ／
６０〔Ｈｚ〕となり、この領域内に回転子１の固有振動
数ｆo が存在すると、軸受７、８を支点とした回転子１
の共振が発生し、上記したように、回転子軸１ａが大き
く振られて回転子軸に固定されているスリップリング３
ａ、３ｂの摺動面が振れ、ブラシ４ｂ、４ｃとの接触が
不安定になり、発電機の出力電流のふらつきや出力電流
の低下、さらには摺動面荒れによるスリップリング３
ａ、３ｂとブラシ４ｂ、４ｃの早期摩耗の虞れを生じ
る。By the way, when the AC generator ACG and the vacuum pump VP are rotationally driven as described above, vibration of the nth order of rotation with the vacuum pump VP as a vibration source is generated as shown in FIG. . Where n is the number of vanes 13,
Therefore, in this embodiment, as described above, n = 4. Therefore, assuming that the practical maximum rotation speed is N [rpm], in this case, the vibration frequency is 0 [Hz] to n · N /
When the natural frequency fo of the rotor 1 exists within this region, the rotor 1 having the bearings 7 and 8 as the fulcrum is a fulcrum.
Of the slip ring 3 which is fixed to the rotor shaft by vibrating the rotor shaft 1a largely as described above.
The sliding surfaces of a and 3b swing, the contact with the brushes 4b and 4c becomes unstable, the output current of the generator fluctuates, the output current decreases, and the slip ring 3 due to the sliding surface roughening.
There is a risk of early wear of the a, 3b and the brushes 4b, 4c.
【００２３】そこで、この実施例では、回転子１の質量
をｍ〔Ｋｇ〕、回転子の回転軸１ａのヤング率をＥ〔Ｎ
／ｍｍ 2 〕、平均軸径をｄ〔ｍｍ〕、そして図１に示す
ように、回転子１の中心から一方の軸受７の中心までの
回転軸１ａの長さをＬ1〔ｍｍ〕、回転子１の中心から
他方の軸受８の中心までの回転軸１ａの長さをＬ2〔ｍ
ｍ〕、真空ポンプＶＰのベーン１３の個数をｎ、そして
回転子１の最高回転速度をＮ〔ｒｐｍ〕としたとき、回
転子の固有振動数ｆo〔Ｈｚ〕は、Therefore, in this embodiment, the mass of the rotor 1 is m [ Kg ] and the Young's modulus of the rotating shaft 1a of the rotor is E [ N.
/ Mm 2 ], the average shaft diameter is d [mm], and the length of the rotating shaft 1 a from the center of the rotor 1 to the center of one bearing 7 is L 1 [mm], as shown in FIG. The length of the rotary shaft 1a from the center of the child 1 to the center of the other bearing 8 is L 2 [m
m], the number of vanes 13 of the vacuum pump VP is n, and the maximum rotation speed of the rotor 1 is N [rpm], the natural frequency fo [Hz] of the rotor is
【００２４】[0024]
【数２】 [Equation 2]
【００２５】 ここで、平均軸径ｄ＝(１９ｄ1＋ｄ2)／２０ ｄ1：回転軸１ａの軸受７側での軸径 ｄ2：回転軸１ａの軸受８側での軸径 で与えられるという事実を見出し、これからHere, the average shaft diameter d = ( 19 d 1 + d 2 ) / 20 d 1 is the shaft diameter of the rotating shaft 1 a on the bearing 7 side, and the d 2 is the shaft diameter of the rotating shaft 1 a on the bearing 8 side. Found the fact that
【００２６】[0026]
【数１】 [Equation 1]
【００２７】 が満足されるように、ｍ＝２.６０×１０〜4〔Ｋｇ〕 Ｅ＝２.１×１０4〔Ｎ／ｍｍ 2 〕 ｄ1＝２０〔ｍｍ〕 ｄ2＝１７〔ｍｍ〕 Ｌ1＝４１.４〔ｍｍ〕 Ｌ2＝６９.５〔ｍｍ〕 に定めたものである。なお、真空ポンプＶＰのベーン１
３の個数は、上記したように、４である。[0027] As is satisfied, m = 2.60 × 10~ 4 [Kg] E = 2.1 × 10 4 [N / mm 2] d 1 = 20 [mm] d 2 = 17 [mm] L 1 = 41.4 [mm] L 2 = 69.5 [mm]. The vane 1 of the vacuum pump VP
The number of 3 is 4, as described above.
【００２８】この結果、この実施例によれば、図３に破
線で示すように、回転子１の固有振動数ｆo〔Ｈｚ〕が
かなり高くなり、これと、真空ポンプＶＰを加振源とす
る回転ｎ次振動数ｆn〔Ｈｚ〕とが一致する回転速度
を、１１５００〔ｒｐｍ〕の、実用上充分な最高回転速
度Ｎよりもかなり高い回転速度にすることができ、交流
発電機ＡＣＧにより充分に安定した電力を取り出すこと
ができた。As a result, according to this embodiment, as shown by the broken line in FIG. 3, the natural frequency fo [Hz] of the rotor 1 becomes considerably high, and this and the vacuum pump VP are used as vibration sources. The rotation speed at which the n-th rotation frequency fn [Hz] matches can be set to 11,500 [rpm], which is considerably higher than the practically sufficient maximum rotation speed N, and is sufficiently increased by the AC generator ACG. We were able to extract stable power.
【００２９】一方、図３に実線で示した特性は従来例に
よるものであり、この従来例では、上記実施例とは異な
り、各部の定数や寸法を ｍ＝２.５２×１０〜4〔Ｋｇ〕 Ｅ＝２.１×１０4〔Ｎ／ｍｍ 2 〕 ｄ1＝１７〔ｍｍ〕 ｄ2＝１５〔ｍｍ〕 Ｌ1＝４０.４〔ｍｍ〕 Ｌ2＝７０.０〔ｍｍ〕 に定めたものである。なお、真空ポンプＶＰのベーン１
３の個数は、同じく４である。On the other hand, the characteristics shown by the solid line in FIG. 3 are based on the conventional example. In this conventional example, unlike the above-mentioned example, the constants and dimensions of each part are m = 2.52 × 10 4 [ Kg ] E = 2.1 × 10 4 [ N / mm 2 ] d 1 = 17 [mm] d 2 = 15 [mm] L 1 = 40.4 [mm] L 2 = 70.0 [mm] It is a thing. The vane 1 of the vacuum pump VP
Similarly, the number of 3 is 4.
【００３０】従って、この図３の実線の特性から明らか
なように、この従来例では、回転子の固有振動数ｆo
〔Ｈｚ〕がかなり低くなり、この結果、回転子の固有振
動数ｆo〔Ｈｚ〕と、真空ポンプＶＰを加振源とする回
転ｎ次振動数ｆn〔Ｈｚ〕とが一致する回転速度は、１
１５００〔ｒｐｍ〕の最高回転速度Ｎよりもかなり低い
ところになってしまい、常用回転速度領域内で回転子の
共振を生じ、スリップリングの摺動面が振れ、ブラシと
の接触が不安定になり、発電機の出力電流のふらつきや
出力電流の低下、さらには摺動面荒れによるスリップリ
ングとブラシの早期摩耗の虞れを生じてしまうものであ
る。Therefore, as is clear from the characteristics of the solid line in FIG. 3, in this conventional example, the natural frequency fo of the rotor is
[Hz] becomes considerably low, and as a result, the rotation speed at which the natural frequency fo [Hz] of the rotor and the nth-order rotation frequency fn [Hz] with the vacuum pump VP as the vibration source coincide with each other is 1.
It is much lower than the maximum rotation speed N of 1500 [rpm], the resonance of the rotor occurs in the normal rotation speed region, the sliding surface of the slip ring swings, and the contact with the brush becomes unstable. The fluctuation of the output current of the generator, the decrease of the output current, and the risk of premature wear of the slip ring and the brush due to the roughening of the sliding surface may occur.
【００３１】ところで、本発明は、図２に示す、交流発
電機ＡＣＧの固定子鉄心９の外径寸法Ｄがあまり大きく
なると、上記した条件を満たすのに必要な各部の寸法も
大きくなりすぎ、実用的ではない。従って、本発明の適
用範囲は、この固定子鉄心９の外径寸法Ｄとして、一般
的に汎用されている１４５〔ｍｍ〕以下の交流発電機と
して実施するのが好適である。By the way, according to the present invention, when the outer diameter dimension D of the stator core 9 of the AC generator ACG shown in FIG. 2 becomes too large, the dimensions of each part necessary for satisfying the above condition become too large. Not practical. Therefore, the applicable range of the present invention is preferably implemented as an AC generator having an outer diameter dimension D of the stator core 9 of 145 [mm] or less which is generally used.
【００３２】[0032]
【発明の効果】本発明によれば、偏心形ベーンポンプか
らなる真空ポンプを備えた交流発電機において、回転子
の固有振動数を、加振源となる真空ポンプからの回転ｎ
次振動数よりも高い領域に確実に設定することができる
ので、交流発電機の常用回転速度領域内で回転子軸が共
振してしまうのが充分に抑えられ、回転子軸のふらつき
による励磁電流の変化の虞れが無くなり、常に安定した
出力電流を供給することができる。According to the present invention, in the AC generator equipped with the vacuum pump composed of the eccentric vane pump, the natural frequency of the rotor is changed from the vacuum pump serving as the vibration source to the rotation n.
Since it can be reliably set to a region higher than the next frequency, resonance of the rotor shaft within the normal rotation speed region of the alternator is sufficiently suppressed, and the excitation current due to rotor shaft wobbling. Therefore, there is no fear of change in the output current, and a stable output current can always be supplied.
【００３３】また、この結果、スリップリングの摺動面
荒れの発生を抑えることができるので、耐摩耗性が大幅
に改善され、耐用時間の向上を容易に得ることができ
る。As a result, it is possible to suppress the occurrence of roughening of the sliding surface of the slip ring, so that the wear resistance is greatly improved and the service life can be easily improved.
【図１】本発明による真空ポンプ付交流発電機の一実施
例における回転子の一部断面による側面図である。FIG. 1 is a side view with a partial cross section of a rotor in an embodiment of an AC generator with a vacuum pump according to the present invention.
【図２】本発明による真空ポンプ付交流発電機の一実施
例を示す一部断面による側面図である。FIG. 2 is a partial cross-sectional side view showing an embodiment of an AC generator with a vacuum pump according to the present invention.
【図３】本発明の一実施例の効果を説明するための特性
図である。FIG. 3 is a characteristic diagram for explaining an effect of one embodiment of the present invention.
ＡＣＧ 交流発電機 ＶＰ 真空ポンプ １ 回転子 １ａ 回転子軸 １ｂ セレーション ２ 界磁コイル ３ａ、３ｂ スリップリング ３ｃ フロントカバー ３ｄ リヤカバー ４ａ ブラシ保持器 ４ｂ、４ｃ ブラシ ５ 整流装置 ６ プーリ ７、８ 軸受 ９ 固定子鉄心 ９ａ ３相巻線からなる電機子コイル １０、１０ａ ボルト １１ 真空ポンプＶＰのロータ １２ 真空ポンプＶＰのケーシング １３ 真空ポンプＶＰのベーン ACG AC generator VP Vacuum pump 1 Rotor 1a Rotor shaft 1b Serration 2 Field coil 3a, 3b Slip ring 3c Front cover 3d Rear cover 4a Brush holder 4b, 4c Brush 5 Rectifier 6 Pulley 7, 8 Bearing 9 Stator Iron core 9a Armature coil consisting of three-phase winding 10, 10a Volt 11 Rotor of vacuum pump VP 12 Casing of vacuum pump VP 13 Vane of vacuum pump VP
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭59−44947（ＪＰ，Ａ) 特開 昭52−5409（ＪＰ，Ａ) 実開 昭61−7245（ＪＰ，Ｕ) ─────────────────────────────────────────────────── ─── Continuation of the front page (56) References JP-A-59-44947 (JP, A) JP-A-52-5409 (JP, A) Actually-opened Sho-61-7245 (JP, U)
Claims (2)
の軸端に偏心形ベーンポンプからなる真空ポンプのロー
タが取付けられた回転界磁型交流発電機において、上記
回転子の質量をｍ〔Ｋｇ〕、上記回転子の回転軸のヤン
グ率をＥ〔Ｎ／ｍｍ 2 〕、平均軸径をｄ〔ｍｍ〕、上記
回転子の中心から上記一方の軸受の中心までの軸の長さ
をＬ1〔ｍｍ〕、上記回転子の中心から他方の軸受の中
心までの軸の長さをＬ2〔ｍｍ〕、上記真空ポンプのベ
ーンの個数をｎ、上記回転子の最高回転速度をＮ〔ｒｐ
ｍ〕としたとき、次の式が成立するように構成したこと
を特徴とする真空ポンプ付交流発電機。 【数１】 1. A rotary field AC generator in which a rotor of a vacuum pump composed of an eccentric vane pump is attached to an outer shaft end of one bearing of a double-shaft double-bearing rotor, and the mass of the rotor is m [ Kg ], Young's modulus of the rotating shaft of the rotor is E [ N / mm 2 ], average shaft diameter is d [mm], and the length of the shaft from the center of the rotor to the center of the one bearing. Is L 1 [mm], the length of the shaft from the center of the rotor to the center of the other bearing is L 2 [mm], the number of vanes of the vacuum pump is n, and the maximum rotation speed of the rotor is N. [Rp
m], the alternating current generator with a vacuum pump is configured such that the following equation is satisfied. [Equation 1]
機の電機子鉄心の外径寸法が１４５〔ｍｍ〕以下である
ことを特徴とする真空ポンプ付交流発電機。2. The AC generator with a vacuum pump according to claim 1, wherein the armature core of the AC generator has an outer diameter of 145 [mm] or less.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3230774A JPH088756B2 (en) | 1991-08-19 | 1991-08-19 | AC generator with vacuum pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3230774A JPH088756B2 (en) | 1991-08-19 | 1991-08-19 | AC generator with vacuum pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0556602A JPH0556602A (en) | 1993-03-05 |
| JPH088756B2 true JPH088756B2 (en) | 1996-01-29 |
Family
ID=16913056
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3230774A Expired - Fee Related JPH088756B2 (en) | 1991-08-19 | 1991-08-19 | AC generator with vacuum pump |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH088756B2 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5845954A (en) * | 1996-06-25 | 1998-12-08 | Toyota Technical Center, U.S.A., Inc. | Glove box assembly including glove box that is positionable in a partially open position |
| JP4046037B2 (en) | 2003-07-22 | 2008-02-13 | 豊田合成株式会社 | Drawer device |
| CN107885699A (en) * | 2017-09-26 | 2018-04-06 | 昆明理工大学 | A kind of method for the shafting vibration throw analytical expression for establishing vertical water pump shaft system of unit track |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS525409A (en) * | 1975-07-02 | 1977-01-17 | Nippon Denso Co Ltd | Generator with oil rotation vacuum pump |
| JPS5944947A (en) * | 1982-09-03 | 1984-03-13 | Nippon Denso Co Ltd | Generator with eccentric vacuum pump |
| JPS617245U (en) * | 1984-06-15 | 1986-01-17 | 株式会社日立製作所 | Oil intrusion prevention device for oil-supplied vacuum pump direct-coupled generators |
-
1991
- 1991-08-19 JP JP3230774A patent/JPH088756B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0556602A (en) | 1993-03-05 |
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