JPH08243296A - Rotating drive mechanism for electrical washing machine - Google Patents
Rotating drive mechanism for electrical washing machineInfo
- Publication number
- JPH08243296A JPH08243296A JP7050203A JP5020395A JPH08243296A JP H08243296 A JPH08243296 A JP H08243296A JP 7050203 A JP7050203 A JP 7050203A JP 5020395 A JP5020395 A JP 5020395A JP H08243296 A JPH08243296 A JP H08243296A
- Authority
- JP
- Japan
- Prior art keywords
- end surface
- main shaft
- outer cylinder
- bearing metal
- flange
- 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
Links
Classifications
-
- 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
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H2057/085—Bearings for orbital gears
Landscapes
- General Details Of Gearings (AREA)
- Mounting Of Bearings Or Others (AREA)
- Main Body Construction Of Washing Machines And Laundry Dryers (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は、一槽式電気洗濯機の
洗濯槽およびパルセータを回転駆動させる電気洗濯機の
回転駆動機構に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary drive mechanism of an electric washing machine for rotating a washing tub and a pulsator of a single-tub electric washing machine.
【０００２】[0002]
【従来の技術】一槽式電気洗濯機は、洗濯と脱水を単一
槽内で連続式で行うもので、通常、洗濯・すすぎ時には
脱水槽の底部に設けられたパルセータのみが低速回転し
て衣料のもみ洗いを行い、脱水時にはパルセータと脱水
槽が一体的に高速回転して衣料を遠心脱水するようにな
っている。2. Description of the Related Art A single-tub electric washing machine performs washing and dewatering continuously in a single tub, and normally only the pulsator provided at the bottom of the dewatering tub rotates at low speed during washing and rinsing. When the clothes are washed with rice, the pulsator and the dehydration tub rotate together at high speed to spin-dry the clothes.
【０００３】すなわち、一般的な一槽式電気洗濯機で
は、例えば図４に示すように、脱水槽１０とパルセータ
１１を回転させるメインシャフト１２の、小径に形成さ
れた下部に、ボス２３を介してワンウェイバネクラッチ
１４が取り付けられており、プーリ２０を介してこのワ
ンウェイバネクラッチ１４が締まる方向に回転駆動が与
えられると、メインシャフト１２に外嵌された外筒１３
が、メインシャフト１２と一体的に高速回転するように
なっている。なお、上記メインシャフト１２の中央部
は、外筒１３の内側に圧入された上下２個の軸受メタル
３０，３１によって回転自在に支受されている。上記高
速回転は、メインシャフト１２の上部に形成された太陽
歯車軸１２ａから減速手段（遊星歯車群１７およびこれ
と噛み合う外輪歯車２２）を内蔵したギヤケース１５に
伝達され、ギヤケース１５から上方に延びるガイド筒１
６を介して脱水槽１０に伝達される。これにより、脱水
動作が行われる。一方、プーリ２０を介して上記ワンウ
ェイバネクラッチ１４が緩む方向に回転駆動が与えられ
ると、外筒１３は回転せず、メインシャフト１２のみが
回転する。この回転は、ギヤケース１５内の遊星歯車群
１７に伝達され、減速された回転がパルセータシャフト
１９に伝達される。これにより、パルセータシャフト１
９上端に取り付けられたパルセータ１１が低速回転し、
洗濯・すすぎ動作が行われる。なお、１８は遊星歯車群
１７を一体的に保持する蓋部である。That is, in a general one-tub type electric washing machine, as shown in FIG. 4, for example, a boss 23 is interposed below a small-diameter lower portion of a main shaft 12 for rotating a dehydration tub 10 and a pulsator 11. When the one-way spring clutch 14 is attached to the main shaft 12, the one-way spring clutch 14 is attached to the main shaft 12.
However, the main shaft 12 and the main shaft 12 rotate together at a high speed. The central portion of the main shaft 12 is rotatably supported by two upper and lower bearing metals 30 and 31 press-fitted inside the outer cylinder 13. The high-speed rotation is transmitted from the sun gear shaft 12a formed on the upper portion of the main shaft 12 to the gear case 15 incorporating the speed reducing means (the planetary gear group 17 and the outer ring gear 22 meshing with the planetary gear group 17), and extends upward from the gear case 15. Tube 1
It is transmitted to the dehydration tank 10 via 6. As a result, the dehydration operation is performed. On the other hand, when the one-way spring clutch 14 is rotationally driven through the pulley 20 in the direction of loosening, the outer cylinder 13 does not rotate, but only the main shaft 12 rotates. This rotation is transmitted to the planetary gear group 17 in the gear case 15, and the decelerated rotation is transmitted to the pulsator shaft 19. This allows the pulsator shaft 1
9 The pulsator 11 attached to the upper end rotates at low speed,
Washing and rinsing operations are performed. Reference numeral 18 denotes a lid portion that integrally holds the planetary gear group 17.
【０００４】このような回転駆動機構では、従来から、
駆動を伝達する各歯車（メインシャフト１２の太陽歯車
軸１２ａ，遊星歯車群１７，外輪歯車２２）として、歯
が軸に対し平行な平歯車が用いられてきたが、近年、洗
濯量の増大，脱水の高速化等に伴い、減速比率が増大傾
向にあるため、歯車強度の向上，回転音の静粛化等の諸
要求に応える必要から、各歯車を、図４に示すように、
ハスバ歯車にすることが行われている。In such a rotary drive mechanism, conventionally,
A spur gear whose teeth are parallel to the shaft has been used as each gear (the sun gear shaft 12a of the main shaft 12, the planetary gear group 17, the outer ring gear 22) for transmitting the drive, but in recent years, the amount of washing increases, Since the deceleration ratio tends to increase with the speedup of dehydration, etc., it is necessary to meet various demands such as improvement of gear strength and quietness of rotation noise.
Hasha gear is used.
【０００５】[0005]
【発明が解決しようとする課題】ところが、上記のよう
に、各歯車をハスバ歯車にした場合、洗濯・すすぎ動作
のためにパルセータ１１の正転，逆転運転を行うと、メ
インシャフト１２の太陽歯車軸１２ａと遊星歯車群１７
とが斜めに噛み合っているためメインシャフト１２にス
ラスト力が発生し、反転するたびにメインシャフト１２
が、設定された隙間（図６においてδで示す）分だけ上
下動する。そして、メインシャフト１２が浮き上がると
メインシャフト１２の下部に取り付けられたボス２３の
上端面と外筒１３の下端面１３ａとが衝突し、メインシ
ャフト１２が浮き上がった状態から落下すると軸受メタ
ル３０の上端面３０ａと太陽歯車軸１２ａが形成された
段差端面１２ｂとが衝突して、衝突音を繰り返すことに
なる。However, as described above, when the respective gears are helical gears and the pulsator 11 is rotated in the forward and reverse directions for washing and rinsing operations, the sun gear of the main shaft 12 is rotated. Shaft 12a and planetary gear group 17
The thrust force is generated in the main shaft 12 because the and are meshed diagonally, and the main shaft 12
Moves up and down by the set gap (indicated by δ in FIG. 6). When the main shaft 12 floats up, the upper end surface of the boss 23 attached to the lower part of the main shaft 12 collides with the lower end surface 13a of the outer cylinder 13, and when the main shaft 12 falls from the floating state, the bearing metal 30 tops up. The end face 30a collides with the step end face 12b on which the sun gear shaft 12a is formed, and the collision sound is repeated.
【０００６】そこで、この衝突音を低く抑えるために、
上記隙間δをできるだけ小さく設定することが必要とな
るが、設計，製作の段階で隙間δを最小限に決定するこ
とは困難なため、組み立て時に一品ずつ個別に調整して
いるのが実情である。調整方法としては、つぎの二通り
の方法がある。Therefore, in order to suppress the collision noise to a low level,
It is necessary to set the gap δ as small as possible, but it is difficult to determine the gap δ to the minimum at the stage of designing and manufacturing. Therefore, it is the actual situation that each product is individually adjusted during assembly. . There are the following two adjustment methods.
【０００７】 図６に示すように、外筒１３の、軸受
メタル３０，３１が圧入される部分の長さ（以下「軸受
部の長さ」という）Ｓと、軸受メタル３０および３１の
フランジ厚Ａ，Ｂをそれぞれ測定するとともに、メイン
シャフト１２の、外筒１３と嵌合する中央部１２ｃの長
さ寸法Ｌを測定し、Ｓ＋Ａ＋Ｂ＋１（軸受メタル３１の
入り込み代、図６では１ｍｍ）の長さと上記Ｌとを比較
する。そして、図７に示すように、軸受メタル３０上端
面とメインシャフト１２の太陽歯車軸１２ａ形成部との
間に、燐青銅スラストワッシャ４０を挟むこととし、こ
の燐青銅スラストワッシャ４０として厚さの異なる数種
類を用意しておくことにより、適宜の厚さの燐青銅スラ
ストワッシャ４０を選択して隙間δの寸法が０．０５±
０．０２ｍｍになるよう調整する。As shown in FIG. 6, the length S of the outer cylinder 13 into which the bearing metals 30 and 31 are press fitted (hereinafter referred to as “bearing length”) S and the flange thickness of the bearing metals 30 and 31. In addition to measuring A and B, the length L of the central portion 12c of the main shaft 12 that fits with the outer cylinder 13 is measured, and the length of S + A + B + 1 (the insertion margin of the bearing metal 31, 1 mm in FIG. 6) is measured. Compare with L above. Then, as shown in FIG. 7, a phosphor bronze thrust washer 40 is sandwiched between the upper end surface of the bearing metal 30 and the sun gear shaft 12a forming portion of the main shaft 12, and the phosphor bronze thrust washer 40 has a different thickness. By preparing several different types, a phosphor bronze thrust washer 40 having an appropriate thickness is selected, and the size of the gap δ is 0.05 ±.
Adjust to 0.02 mm.
【０００８】 外筒１３に軸受メタル３０，３１を圧
入し、図７に示すように、上部に燐青銅スラストワッシ
ャ４０を挟み（この場合、ワッシャ４０の厚さは一種類
でよい）、図８に示すように、下部に樹脂系スラストワ
ッシャ４１を挟んだ状態でメインシャフト１２を外筒１
３とを組み立て、さらにボス２３を取り付けることと
し、その際、上記ボス２３の上端面に、メインシャフト
１２の中央部１２ｃの下部が入り込む段差２３ａを形成
しておき、この段差２３ａの深さが異なるものを数種類
用意しておくことにより、適宜のボス２３を選択して隙
間δの寸法が０．０５±０．０２ｍｍになるよう調整す
る。The bearing metals 30 and 31 are press-fitted into the outer cylinder 13, and a phosphor bronze thrust washer 40 is sandwiched between them as shown in FIG. 7 (in this case, the washer 40 may be of one type of thickness). As shown in FIG. 2, the main shaft 12 is attached to the outer cylinder 1 with the resin type thrust washer 41 sandwiched in the lower part.
3 is assembled and the boss 23 is further attached. At this time, a step 23a into which the lower part of the central portion 12c of the main shaft 12 is inserted is formed on the upper end surface of the boss 23, and the depth of the step 23a is By preparing several different types, an appropriate boss 23 is selected and the dimension of the gap δ is adjusted to be 0.05 ± 0.02 mm.
【０００９】このように、一品ごとに隙間δを調整する
ことは非常に煩雑な手間を要するため、作業能率が悪
く、また調整ミスにより衝突音が発生する不良品が出回
るおそれもあり、その改良が強く望まれている。As described above, since adjusting the gap δ for each product requires a very complicated labor, the work efficiency is poor, and there is also a possibility that a defective product which causes a collision noise due to an adjustment error may appear on the market. Is strongly desired.
【００１０】この発明は、このような事情に鑑みなされ
たもので、一品ごとに隙間調整を行う必要のない、組み
立て作業効率に優れた電気洗濯機の回転駆動機構の提供
をその目的とする。The present invention has been made in view of the above circumstances, and an object thereof is to provide a rotary drive mechanism of an electric washing machine which does not require a gap adjustment for each product and is excellent in assembling work efficiency.
【００１１】[0011]
【課題を解決するための手段】上記の目的を達成するた
め、この発明の電気洗濯機の回転駆動機構は、上部が中
央部より大径の太陽歯車軸に形成され下部が中央部より
小径のプーリ取り付け部に形成されたメインシャフト
と、上記メインシャフトの中央部を回転自在に支受する
上下２個の軸受メタルが圧入された外筒と、上記メイン
シャフトの太陽歯車軸と噛み合ってその回転を減速する
減速手段と、上記減速手段を内蔵するとともに上記外筒
と一体的に回転しその回転力によって脱水槽を回転させ
るギヤケースと、上記減速手段によって減速された回転
が伝達されその回転力によってパルセータを回転させる
パルセータシャフトとを備え、上記外筒に圧入されたメ
タル軸受のうち少なくとも上側の軸受メタルがフランジ
部を有し、そのフランジ部下端面と上記外筒の上端面と
の間に調整リングが挟持されており、この調整リングが
フランジ付軸受メタル圧入時の圧力で上下方向に潰され
ることによって、フランジ付軸受メタル上端面から外筒
下端面までの長さ寸法に設定隙間寸法を加算した値が、
メインシャフト中央部の長さ寸法と等しくなるよう調整
されているという構成をとる。To achieve the above object, a rotary drive mechanism for an electric washing machine according to the present invention has an upper part formed on a sun gear shaft having a larger diameter than the central part and a lower part having a smaller diameter than the central part. The main shaft formed in the pulley mounting portion, the outer cylinder into which the upper and lower two bearing metals that rotatably support the central portion of the main shaft are press-fitted, and the sun gear shaft of the main shaft meshes and rotates. Decelerating means for decelerating, a gear case that incorporates the decelerating means and that rotates integrally with the outer cylinder and rotates the dehydration tub by its rotational force, and the rotation decelerated by the decelerating means is transmitted by the rotational force. A pulsator shaft for rotating the pulsator, and at least the upper bearing metal of the metal bearing press-fitted into the outer cylinder has a flange portion, An adjusting ring is sandwiched between the lower end surface of the flange and the upper end surface of the outer cylinder.The adjusting ring is crushed in the vertical direction by the pressure when the bearing metal with flange is press-fitted, so that The value obtained by adding the set clearance dimension to the length dimension to the lower surface of the outer cylinder is
The length is adjusted to be equal to the central length of the main shaft.
【００１２】[0012]
【作用】すなわち、この発明は、従来のように、外筒軸
受部とメインシャフト中央部との間に形成される隙間寸
法を、挿入するワッシャの厚さ等で、一品ごとにいちい
ち調整するのではなく、外筒に軸受メタルを圧入する際
に、上側のフランジ付軸受メタルのフランジ部下端面と
外筒の上端面との間に調整リングを挟み、これを軸受メ
タル圧入時の圧力で塑性変形させて潰し、フランジ付軸
受メタル圧入後の、そのフランジ部上端面から外筒下端
面までの長さ寸法に設定隙間寸法を加算した値を、この
部分に嵌合するメインシャフト中央部の長さ寸法に一致
させるようにしたものである。したがって、この構成に
よれば、調整リングを挟むという画一的、かつ簡単な動
作を付加するだけで、大きな衝突音が生じる設定値以上
の隙間δ（図６参照）の形成を解消することができ、従
来のような、一品ごとの煩雑な隙間調整作業が不要とな
る。That is, according to the present invention, the gap size formed between the outer cylindrical bearing portion and the central portion of the main shaft is individually adjusted for each product by the thickness of the washer to be inserted, etc. Instead, when press-fitting the bearing metal into the outer cylinder, insert an adjustment ring between the lower end surface of the flange of the bearing metal with upper flange and the upper end surface of the outer cylinder, and plastically deform this with the pressure when press-fitting the bearing metal. After crushing and press-fitting the bearing metal with flange, add the set clearance dimension to the length dimension from the upper end face of the flange to the lower end face of the outer cylinder, and then set the length of the center part of the main shaft that fits in this part. It is designed to match the dimensions. Therefore, according to this configuration, it is possible to eliminate the formation of the gap δ (see FIG. 6) that is equal to or larger than the set value at which a large collision sound is generated, only by adding a uniform and simple operation of sandwiching the adjustment ring. Therefore, it is not necessary to perform a complicated gap adjusting operation for each product as in the conventional case.
【００１３】つぎに、この発明を実施例にもとづいて詳
細に説明する。Next, the present invention will be described in detail based on embodiments.
【００１４】[0014]
【実施例】図１はこの発明の一実施例の要部を示してい
る。すなわち、この電気洗濯機の回転駆動機構は、基本
的には図４の構成と同一であり、図４と同一部分に同一
番号を付しているが、この機構では、外筒１３の上部に
圧入されたフランジ付軸受メタル３０のフランジ部下端
面と外筒１３の上端面との間に、アルミニウム製の調整
リング５０が挟持されている。そして、上記調整リング
５０は、上記フランジ付軸受メタル３０を外筒１３に圧
入する際の圧力によって上下方向に塑性変形して潰れ、
フランジ付軸受メタル３０の上端面から外筒１３の下端
面までの長さ寸法Ｍ（図２参照）に、設定隙間寸法を加
算した値が、この部分と嵌合するメインシャフト１２の
中央部の長さ寸法Ｌ（図１参照）と等しくなるよう設定
されている。DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows the essential parts of an embodiment of the present invention. That is, the rotary drive mechanism of this electric washing machine is basically the same as the configuration of FIG. 4, and the same parts as those in FIG. 4 are denoted by the same reference numerals. An adjustment ring 50 made of aluminum is sandwiched between the lower end surface of the flange portion of the flanged bearing metal 30 and the upper end surface of the outer cylinder 13. Then, the adjusting ring 50 is plastically deformed in the vertical direction by the pressure when the flanged bearing metal 30 is press-fitted into the outer cylinder 13, and is crushed,
The value obtained by adding the set clearance dimension to the length dimension M (see FIG. 2) from the upper end surface of the flanged bearing metal 30 to the lower end surface of the outer cylinder 13 is the value of the central portion of the main shaft 12 fitted with this portion. It is set to be equal to the length dimension L (see FIG. 1).
【００１５】上記外筒１３側の長さ寸法Ｍに設定隙間寸
法を加算した値が、メインシャフト１２側の長さ寸法Ｌ
に等しくなるように調整リング５０を潰すには、調整リ
ング５０を挟持した状態でフランジ付軸受メタル３０を
外筒１３に圧入する際に、図２に示すように、外筒１３
下端面を基準面Ｘとし、メインシャフト１２の中央部の
長さＬから設定隙間寸法を減じた寸法に一致する高さ
に、フランジ付軸受メタル３０の上端面がくるよう圧入
プレスを行うようにする。これにより、従来寸法精度が
得られなかったフランジ付軸受メタル３０圧入後の寸法
Ｍが、調整リング５０の潰れ具合によって画一的にメイ
ンシャフト１２側の寸法Ｌから設定隙間寸法を減じた寸
法と一致するようになる。このようにしてフランジ付軸
受メタル３０が圧入された外筒１３にメインシャフト１
２を組み込むと、外筒１３の下端面１３ａとボス２３の
上端面との間に形成される隙間δ（図６参照）の寸法が
最小限の設定値に限定されるため、衝突音が発生するこ
とがない。したがって、従来のように、一品ごとに隙間
調整を行う必要がない。A value obtained by adding the set clearance dimension to the length dimension M on the outer cylinder 13 side is the length dimension L on the main shaft 12 side.
In order to crush the adjustment ring 50 so as to be equal to, when the bearing metal with flange 30 is press-fitted into the outer cylinder 13 while holding the adjustment ring 50, as shown in FIG.
The press-fitting press is performed so that the upper end surface of the flanged bearing metal 30 comes to a height corresponding to the length L of the central portion of the main shaft 12 minus the set clearance dimension with the lower end surface as the reference plane X. To do. As a result, the dimension M after the press-fitting of the flanged bearing metal 30 for which the conventional dimensional accuracy has not been obtained is a dimension obtained by uniformly subtracting the set clearance dimension from the dimension L on the main shaft 12 side due to the crushing condition of the adjustment ring 50. Will come to match. In this way, the main shaft 1 is inserted into the outer cylinder 13 in which the bearing metal with flange 30 is press-fitted.
When 2 is incorporated, the size of the gap δ (see FIG. 6) formed between the lower end surface 13a of the outer cylinder 13 and the upper end surface of the boss 23 is limited to the minimum set value, so that a collision sound is generated. There is nothing to do. Therefore, it is not necessary to adjust the gap for each product as in the conventional case.
【００１６】なお、この発明では、調整リング５０を上
下方向に潰して、フランジ付軸受メタル３０の上端面か
ら外筒１３の下端面までの長さ寸法Ｍに設定隙間寸法を
加算した値が、この部分と嵌合するメインシャフト１２
の中央部の長さ寸法Ｌと等しくなるようにすることが最
大の特徴であるが、上記「設定隙間寸法」とは、隙間δ
の寸法が、メインシャフト１２のがたつきによって衝突
音が発生しない程度、すなわち、０．０５±０．０２ｍ
ｍ以下に設定されることをいう。In the present invention, the adjustment ring 50 is crushed in the vertical direction, and the value obtained by adding the set clearance dimension to the length dimension M from the upper end surface of the flanged bearing metal 30 to the lower end surface of the outer cylinder 13 is Main shaft 12 that fits with this part
The greatest feature is to make it equal to the length dimension L of the central part of the.
Is such that the rattling of the main shaft 12 does not generate a collision noise, that is, 0.05 ± 0.02 m.
It is set to m or less.
【００１７】また、上記実施例では、調整リング５０と
してアルミニウム製のものを用いているが、その材質
は、塑性変形して潰れやすいものであればどのようなも
のであっても差し支えはない。例えば、銅、アルミルウ
ムと銅の合金、あるいは樹脂等を用いることができる。In the above embodiment, the adjustment ring 50 is made of aluminum, but any material may be used as long as it is plastically deformable and easily crushed. For example, copper, an alloy of aluminum and copper, a resin, or the like can be used.
【００１８】さらに、上記実施例では、外筒１３の上下
に圧入する軸受メタル３０，３１はともにフランジ付で
あるが、下方の軸受メタル３１は必ずしもフランジ付で
なくても差し支えはない。Further, in the above embodiment, both the bearing metals 30 and 31 press-fitted in the upper and lower parts of the outer cylinder 13 are provided with flanges, but the lower bearing metal 31 may not necessarily be provided with flanges.
【００１９】ちなみに、上記調整リング５０を用いるこ
とによって隙間δの寸法が調整不要な程度に小さくなる
ことを検証するために、下記の条件で実験を行った。 ・外筒１３の軸受部長さＳ（図３参照）＝５９．０ｍｍ
（公差０〜＋０．０５） ・フランジ付軸受メタル３０のフランジ厚さＡ＝１．９
８ｍｍ（実測値、焼結金属のため寸法誤差０．０１ｍｍ
以内） ・シム厚さＨは、１０．２０ｍｍ，９．５９ｍｍ，９．
１９ｍｍの３種類 ・調整リング５０の厚さは、１．０ｍｍ，１．６ｍｍ，
２．０ｍｍの３種類 ・上記外筒１３に嵌合させるメインシャフト１２の中央
部の長さＬは、６１．９８ｍｍ，６２．５８ｍｍ，６
２．９８ｍｍの３種類Incidentally, in order to verify that the size of the gap δ is reduced to the extent that adjustment is unnecessary by using the adjusting ring 50, an experiment was conducted under the following conditions.・ The bearing length S of the outer cylinder 13 (see FIG. 3) = 59.0 mm
(Tolerance 0 to +0.05) -Flange thickness A of bearing metal 30 with flange A = 1.9
8mm (measured value, dimensional error 0.01mm due to sintered metal)
・ The shim thickness H is 10.20 mm, 9.59 mm, 9.
19 mm 3 types ・ The thickness of the adjustment ring 50 is 1.0 mm, 1.6 mm,
Three types of 2.0 mm-The length L of the central portion of the main shaft 12 fitted into the outer cylinder 13 is 61.98 mm, 62.58 mm, 6
2.98mm 3 types
【００２０】以上の条件で、図３に示すように、外筒１
３に調整リング５０を挟み、その上からフランジ付軸受
メタル３０を圧入する金型プレス機５１を組み立てた。
５２は上型で、下面５２ａの中央から下向きに、フラン
ジ付軸受メタル３０の上端面を押圧する円柱部５２ｂが
突出形成されており、さらにその中央から、軸受メタル
３０に挿通されるガイドシャフト５３が垂下している。
また、５４は下型で、シム５５の上に基台５６が取り付
けられ、周囲にガイド筒５７が設けられている。上記上
型５２の下面５２ａと、下型５４のガイド筒５７上端面
５７ａとの隙間が、調整リング５０のつぶし代Ｐとな
る。また、下型５４の基台５６上面５６ａが基準面とな
る。そして、シム５５の厚さおよび調整リング５０の厚
さを変えることにより、上記つぶし代Ｐの寸法および圧
入後のＭ寸法を変えることができる。Under the above conditions, as shown in FIG. 3, the outer cylinder 1
A mold pressing machine 51 was assembled in which the adjustment ring 50 was sandwiched in 3 and the bearing metal with flange 30 was press-fitted from above.
52 is an upper die, and a columnar portion 52b that presses the upper end surface of the flanged bearing metal 30 is formed so as to project downward from the center of the lower surface 52a. Further, from the center, a guide shaft 53 that is inserted into the bearing metal 30 is formed. Is hanging.
A lower die 54 has a base 56 mounted on a shim 55 and a guide cylinder 57 provided around the shim 55. A gap between the lower surface 52a of the upper mold 52 and the upper end surface 57a of the guide cylinder 57 of the lower mold 54 serves as a crushing margin P of the adjustment ring 50. Further, the upper surface 56a of the base 56 of the lower mold 54 serves as a reference surface. By changing the thickness of the shim 55 and the thickness of the adjusting ring 50, the size of the crushing margin P and the M size after press fitting can be changed.
【００２１】上記金型プレス機５１によって調整リング
５０をつぶしながらフランジ付軸受メタル３０の圧入を
行い、圧入前後の軸受メタル３０の内径寸法の変化を測
定した。また、軸受メタル３０の抜き力が確保されてい
るかを確認するために、抜き力を測定した。圧入プレス
は１０ｔｏｎロードセルによって圧入力表示を行い、抜
き力は５００ｋｇロードセルによって抜き力表示を行っ
た。これらの結果を下記の表１に示した。The bearing metal 30 with a flange was press-fitted while the adjustment ring 50 was crushed by the die press machine 51, and the change in the inner diameter of the bearing metal 30 before and after the press-fitting was measured. Further, the pulling force was measured in order to confirm whether the pulling force of the bearing metal 30 is secured. In the press-fitting press, a pressure input was displayed by a 10 ton load cell, and a pulling force was displayed by a 500 kg load cell. The results are shown in Table 1 below.
【００２２】[0022]
【表１】 [Table 1]
【００２３】上記の表１から、調整リング５０をつぶし
ながらフランジ付軸受メタル３０を圧入することは、特
に問題がなく、全体として良好な結果が得られることが
わかる。It can be seen from Table 1 above that pressing the flanged bearing metal 30 while crushing the adjusting ring 50 does not cause any particular problems, and good results can be obtained as a whole.
【００２４】[0024]
【発明の効果】以上のように、この発明の電気洗濯機の
回転駆動機構は、外筒に軸受メタルを圧入する際に、上
側のフランジ付軸受メタルのフランジ部下端面と外筒の
上端面との間に調整リングを挟み、これを軸受メタル圧
入時の圧力で塑性変形させて潰し、フランジ付軸受メタ
ル圧入後の、そのフランジ部上端面から外筒下端面まで
の長さ寸法に設定隙間寸法を加算した値を、この部分に
嵌合するメインシャフト中央部の長さ寸法に一致させる
ようにしたものである。したがって、この構成によれ
ば、調整リングを挟むという画一的、かつ簡単な動作を
付加するだけで、衝突音が出る隙間δ（図６参照）の形
成を最小限の寸法に設定することができ、異音の生じな
い良好な製品が確実に得られる。そして、従来のような
一品ごとの煩雑な隙間調整作業が不要となるため、製造
効率が大幅に向上する。As described above, the rotary drive mechanism of the electric washing machine according to the present invention, when the bearing metal is press-fitted into the outer cylinder, causes the lower end surface of the flange portion of the bearing metal with the upper flange and the upper end surface of the outer cylinder to come into contact with each other. Insert an adjustment ring between the two, and crush it by plastically deforming it with the pressure when the bearing metal is pressed in, and set the length between the upper end surface of the flange and the lower end surface of the outer cylinder after press-fitting the flanged bearing metal. The value obtained by adding is made to match the length dimension of the central portion of the main shaft fitted to this portion. Therefore, according to this configuration, it is possible to set the formation of the gap δ (see FIG. 6) at which the collision sound is generated to the minimum size only by adding the uniform and simple operation of sandwiching the adjustment ring. As a result, a good product without abnormal noise is surely obtained. Further, since the complicated gap adjusting work for each product as in the conventional case is not required, the manufacturing efficiency is significantly improved.
【図面の簡単な説明】[Brief description of drawings]
【図１】この発明の一実施例の要部を示す縦断面図であ
る。FIG. 1 is a vertical sectional view showing a main part of an embodiment of the present invention.
【図２】上記実施例の利点の説明図である。FIG. 2 is an explanatory diagram of advantages of the above embodiment.
【図３】上記実施例の検証実験の説明図である。FIG. 3 is an explanatory diagram of a verification experiment of the above embodiment.
【図４】従来の電気洗濯機の回転駆動機構を示す縦断面
図である。FIG. 4 is a vertical sectional view showing a rotation drive mechanism of a conventional electric washing machine.
【図５】ハスバ歯車を用いた構造の分解斜視図である。FIG. 5 is an exploded perspective view of a structure using a helical gear.
【図６】ハスバ歯車を用いた場合の問題点の説明図であ
る。FIG. 6 is an explanatory diagram of a problem when a helical gear is used.
【図７】上記問題点に対する従来の調整方法の一例を示
す部分的な断面図である。FIG. 7 is a partial cross-sectional view showing an example of a conventional adjustment method for the above problems.
【図８】上記問題点に対する従来の調整方法の他の例を
示す部分的な断面図である。FIG. 8 is a partial cross-sectional view showing another example of a conventional adjusting method for the above problems.
１２ メインシャフト １２ａ 中央部 １３ 外筒 ３０ フランジ付軸受メタル ３１ 軸受メタル ５０ 調整リング 12 main shaft 12a central part 13 outer cylinder 30 bearing metal with flange 31 bearing metal 50 adjusting ring
Claims (2)
成され下部が中央部より小径のプーリ取り付け部に形成
されたメインシャフトと、上記メインシャフトの中央部
を回転自在に支受する上下２個の軸受メタルが圧入され
た外筒と、上記メインシャフトの太陽歯車軸と噛み合っ
てその回転を減速する減速手段と、上記減速手段を内蔵
するとともに上記外筒と一体的に回転しその回転力によ
って脱水槽を回転させるギヤケースと、上記減速手段に
よって減速された回転が伝達されその回転力によってパ
ルセータを回転させるパルセータシャフトとを備え、上
記外筒に圧入されたメタル軸受のうち少なくとも上側の
軸受メタルがフランジ部を有し、そのフランジ部下端面
と上記外筒の上端面との間に調整リングが挟持されてお
り、この調整リングがフランジ付軸受メタル圧入時の圧
力で上下方向に潰されることによって、フランジ付軸受
メタル上端面から外筒下端面までの長さ寸法に設定隙間
寸法を加算した値が、メインシャフト中央部の長さ寸法
と等しくなるよう調整されていることを特徴とする電気
洗濯機の回転駆動機構。1. A main shaft having an upper portion formed on a sun gear shaft having a diameter larger than that of a central portion and a lower portion formed on a pulley mounting portion having a diameter smaller than that of the central portion, and a central portion of the main shaft rotatably supported. An outer cylinder in which two upper and lower bearing metals are press-fitted, a speed reducer that meshes with the sun gear shaft of the main shaft to reduce the rotation thereof, and the speed reducer is incorporated and rotates integrally with the outer cylinder. A gear case for rotating the dehydration tank by a rotational force, and a pulsator shaft for rotating the pulsator by the rotational force transmitted by the rotation reduced by the speed reducer are provided. The bearing metal has a flange portion, and an adjustment ring is sandwiched between the lower end surface of the flange portion and the upper end surface of the outer cylinder. Is crushed in the vertical direction by the pressure when the bearing metal with flange is pressed in, and the value obtained by adding the set clearance dimension to the length dimension from the upper end surface of the flanged bearing metal to the lower end surface of the outer cylinder is the length of the center of the main shaft. A rotary drive mechanism for an electric washing machine, wherein the rotary drive mechanism is adjusted to be equal to the size.
０．０２ｍｍである請求項１記載の電気洗濯機の回転駆
動機構。2. The set gap size is 0.05 mm ±
The rotation drive mechanism for an electric washing machine according to claim 1, wherein the rotation drive mechanism is 0.02 mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP05020395A JP3516313B2 (en) | 1995-03-09 | 1995-03-09 | Rotary drive mechanism of electric washing machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP05020395A JP3516313B2 (en) | 1995-03-09 | 1995-03-09 | Rotary drive mechanism of electric washing machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH08243296A true JPH08243296A (en) | 1996-09-24 |
| JP3516313B2 JP3516313B2 (en) | 2004-04-05 |
Family
ID=12852568
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP05020395A Expired - Fee Related JP3516313B2 (en) | 1995-03-09 | 1995-03-09 | Rotary drive mechanism of electric washing machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3516313B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100672497B1 (en) * | 2000-06-21 | 2007-01-23 | 엘지전자 주식회사 | A gear-housing structure in washing-machine |
-
1995
- 1995-03-09 JP JP05020395A patent/JP3516313B2/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100672497B1 (en) * | 2000-06-21 | 2007-01-23 | 엘지전자 주식회사 | A gear-housing structure in washing-machine |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3516313B2 (en) | 2004-04-05 |
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