JP4448401B2 - Composite sintered bearing - Google Patents

Composite sintered bearing Download PDF

Info

Publication number
JP4448401B2
JP4448401B2 JP2004222844A JP2004222844A JP4448401B2 JP 4448401 B2 JP4448401 B2 JP 4448401B2 JP 2004222844 A JP2004222844 A JP 2004222844A JP 2004222844 A JP2004222844 A JP 2004222844A JP 4448401 B2 JP4448401 B2 JP 4448401B2
Authority
JP
Japan
Prior art keywords
bearing
sleeve
bearing member
composite sintered
small diameter
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
Application number
JP2004222844A
Other languages
Japanese (ja)
Other versions
JP2006038185A (en
Inventor
近藤　　誠
俊一 富樫
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.)
Hitachi Powdered Metals Co Ltd
Original Assignee
Hitachi Powdered Metals Co Ltd
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 Hitachi Powdered Metals Co Ltd filed Critical Hitachi Powdered Metals Co Ltd
Priority to JP2004222844A priority Critical patent/JP4448401B2/en
Publication of JP2006038185A publication Critical patent/JP2006038185A/en
Application granted granted Critical
Publication of JP4448401B2 publication Critical patent/JP4448401B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

Landscapes

  • Sliding-Contact Bearings (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Motor Or Generator Frames (AREA)

Description

本発明は、例えば軸流ファンモーターなどの長寿命であることが要求される軸受に好適な、振動、騒音、摩擦損失などの少ない焼結含油軸受（多孔質含油滑り軸受）に関するものである。   The present invention relates to a sintered oil-impregnated bearing (porous oil-impregnated sliding bearing) that is suitable for a bearing that is required to have a long life, such as an axial fan motor, and that has less vibration, noise, friction loss, and the like.

ファンモーターなどの軸受に焼結含油軸受を用いる場合には、軸の振れを防ぐために軸受の長さをある程度大きくする必要がある。然し乍ら長さを増大するに従って、内径面を精度良く一様に仕上げることが困難になり、更に軸受面積の増加に伴い摩擦抵抗も増加するので好ましくない。そこで軸受内径の両端部は所定の寸法に仕上げるとともに、内径の中央部には逃げを設けて、回転軸を両端で支持するのが一般的である。   When using a sintered oil-impregnated bearing for a fan motor or the like, it is necessary to increase the length of the bearing to some extent in order to prevent shaft runout. However, as the length is increased, it becomes difficult to finish the inner diameter surface accurately and uniformly, and the frictional resistance increases as the bearing area increases. Therefore, both ends of the inner diameter of the bearing are finished to a predetermined size, and a relief is provided at the center of the inner diameter to support the rotating shaft at both ends.

この場合、内径の中間に凹部（逃げ）のある円筒体は一体に圧粉成形することはできないが、焼結体への逃げの加工に旋削などの機械加工を施すと切粉による目詰まりや異常摩耗の虞れがある。そこで塑性加工によって逃げ部を形成したり、所望の軸受を型出し可能な形状（円筒の内径が片側は小径で、他の側は大径の段付き孔）の複数の部材に分割してそれぞれを圧粉成形し、両部材の大径側を突き合わせた状態で焼結して一体化するなどの手段が知られているが、工数が増加し、コスト高になるなどの問題がある。さらに、含油軸受用焼結合金は機械部品用焼結合金に比べて一般に軟質なので、機器のハウジングへこのような軸受を圧入する際に、軸受の内径に歪みを生じ易く、その修正加工を要するという問題もある。   In this case, a cylindrical body with a recess (relief) in the middle of the inner diameter cannot be compacted integrally. However, if machining such as turning is performed to process the escape to the sintered body, clogging due to chips will occur. There is a risk of abnormal wear. Therefore, it can be divided into a plurality of members that have a shape that can form relief parts by plastic working or mold a desired bearing (the inner diameter of the cylinder is a small diameter on one side and a large diameter on the other side). There are known means for compacting and sintering and integrating them in a state where the large diameter sides of both members are butted together, but there are problems such as increased man-hours and higher costs. Furthermore, since sintered alloys for oil-impregnated bearings are generally softer than sintered alloys for machine parts, when such a bearing is press-fitted into the housing of a device, the inner diameter of the bearing is likely to be distorted, and a correction process is required. There is also a problem.

また、２個の焼結含油軸受を機器のハウジング内に所定の間隔を明けて装着して回転軸を２点で支持し、両軸受の中間を逃げ部とする方法もある。しかし、この方法では２個の軸受をハウジングに装着した後、両軸受の同軸度を高めるために芯出し加工を行なう必要があり、軸受の組み付けと調整に手間がかかる。   There is also a method in which two sintered oil-impregnated bearings are mounted in the housing of the device at a predetermined interval to support the rotating shaft at two points, and an intermediate portion between both bearings is used as a relief portion. However, in this method, after mounting the two bearings on the housing, it is necessary to perform a centering process in order to increase the coaxiality of the two bearings, and it takes time to assemble and adjust the bearings.

前述の、複数の部材を接合することにより逃げ部を具える軸受を形成する手段の具体例として、実開昭４７−８８４２号公報には図６（ａ）および６（ｂ）に示すように、軸孔が段付き形状の圧粉体６１を２個予め製造し、両者の大内径側同士を突き合わせて鋼管６２内に挿入して焼結することにより、圧粉体と鋼管、および圧粉体同士が一体に焼結接合された、軸孔の両端で回転軸を支持し、中間は逃げ部４２として機能し、外周を鋼管で被覆された焼結含油軸受が得られることが開示されている。この軸受は機器のハウジングに、外皮の鋼管ごと圧入・固定して用いられる。
また、特許第３４７５２１５号公報には、気孔径が互いに異なる２個の焼結軸受部材を嵌め合わせて圧着して得られる、軸受の一方の端部と他方の端部で軸受特性が異なる焼結含油軸受（図７参照）が開示されている。この軸受は、上側の軸受部材６３は高負荷を受ける部材で気孔径の小さな焼結合金であり、下側の軸受部材６４は低負荷を受ける部材で気孔径の大きな焼結合金から作られている。そして上側の軸受部材はその下端部外周側に、下側の軸受部材はその上端部内周側にそれぞれ、相手部材との入れ子組み用の段差部を持つ形状に成形および焼結されたもので、両部材を嵌め合わせて金型内で再圧および芯出しし形成された軸受である。
実開昭４７−８８４２号公報 特許第３４７５２１５号公報 As a specific example of the means for forming a bearing having a relief portion by joining a plurality of members as described above, as shown in FIGS. 6 (a) and 6 (b), Japanese Utility Model Publication No. 47-8842. The two compacts 61 having stepped shaft holes are manufactured in advance, the large inner diameter sides thereof are butted together, inserted into the steel pipe 62, and sintered, whereby the compact, the steel pipe, and the compact It is disclosed that a sintered oil-impregnated bearing is obtained in which the bodies are integrally sintered and bonded, the rotating shaft is supported at both ends of the shaft hole, the middle functions as the escape portion 42, and the outer periphery is covered with a steel pipe. Yes. This bearing is used by press-fitting and fixing the outer steel pipe in the housing of the device.
In addition, Japanese Patent No. 3475215 discloses a sintered bearing having different bearing characteristics at one end of the bearing and the other end obtained by fitting and pressing two sintered bearing members having different pore diameters. An oil-impregnated bearing (see FIG. 7) is disclosed. In this bearing, the upper bearing member 63 is a member that receives a high load and is a sintered alloy having a small pore diameter, and the lower bearing member 64 is a member that receives a low load and is made of a sintered alloy having a large pore diameter. Yes. And the upper bearing member is molded and sintered into a shape having a stepped portion for nesting with the counterpart member on the lower end outer peripheral side, and the lower bearing member on the inner peripheral side of the upper end, It is a bearing formed by fitting both members together and re-pressing and centering in a mold.
Japanese Utility Model Publication No. 47-8842 Japanese Patent No. 3475215

前記の特許文献１に係る軸受の場合は、その外周が鋼管で補強されているので、機器のハウジングへの圧入によって内径面（軸受面）や同軸度に狂いを生じることはないが、軸受から滲み出す潤滑油の回収・循環については格別の機構は設けられていない。
一方、特許文献２に係る軸受の場合は、軸受全体が含油軸受用焼結合金からなる含油量は豊富である反面、これを機器のハウジングに固定する際に、圧入の程度によっては歪みが内径面（軸受面）まで及んで矯正を要することがある。さらに、近年における各種機器の長寿命化、メンテナンスフリー指向および軸受から漏れる潤滑油による周囲の汚染忌避の両面から、軸受の漏油対策に関する要請が一段と厳しくなってきている。本発明はこの様な事情に鑑み、前述の従来技術におけるそれぞれの長所を取り込み、短所は改善し、さらに漏油対策を充実した焼結軸受を提供することを目的とするものである。 In the case of the bearing according to Patent Document 1, since the outer periphery is reinforced with a steel pipe, the inner surface (bearing surface) and the coaxiality are not distorted by press-fitting into the housing of the device. There is no special mechanism for recovery and circulation of the lubricating oil that oozes out.
On the other hand, in the case of the bearing according to Patent Document 2, the entire bearing is rich in oil content made of a sintered alloy for oil-impregnated bearings. However, when the bearing is fixed to the housing of the device, the strain may be reduced depending on the degree of press-fitting. Correction may be required up to the surface (bearing surface). Furthermore, in recent years, demands for measures against oil leakage from bearings have become more severe from the viewpoints of long life of various devices, maintenance-free orientation and avoidance of surrounding contamination by lubricating oil leaking from bearings. In view of such circumstances, an object of the present invention is to provide a sintered bearing that incorporates the respective advantages of the above-described prior art, improves the disadvantages, and further enhances measures against oil leakage.

この発明の複合焼結軸受は、含油軸受用焼結合金からなる軸受２個を、機械部品用焼結合金からなるスリーブの両端部に挿入して固定する。図２は固定方法を例示するもので、図の左側は、再圧用押型５１内に下側の軸受４１、スリーブ２０、上側の軸受４０の順にセットして、コアロッド５２を挿通した状態を示す図である。この状態から、上・下のパンチ５３、５４で圧縮する。軸受は図の右側に示すように、スリーブ２０内に嵌入されて一体に接合すると同時に、上・下の軸受面が所定の寸法および同軸度に仕上げられて所望の複合軸受が得られる。嵌入とは圧入やかしめにより嵌め込むことを言い、以下単に圧入ということもある。また、嵌入操作の前または後に潤滑油が含浸されるのは当然のことである。
この複合軸受においては、スリーブ部材は剛性の高い機械部品用の鉄系焼結合金が適しており、軸受部材はスリーブ部材よりも気孔径の小さい、鉄銅系または青銅系の含油軸受用焼結合金から要求仕様に応じて選択される。なお両端の軸受部材（以下、単に軸受と呼ぶことがある）の中間部、回転軸を装着した場合の軸とスリーブ内面との空隙は、軸受と軸の摺動に関し逃げ部４２として機能する。 In the composite sintered bearing of the present invention, two bearings made of a sintered alloy for oil-impregnated bearings are inserted and fixed to both ends of a sleeve made of a sintered alloy for machine parts. FIG. 2 exemplifies the fixing method, and the left side of the figure shows a state in which the lower bearing 41, the sleeve 20, and the upper bearing 40 are set in this order in the re-pressing die 51 and the core rod 52 is inserted. It is. From this state, compression is performed by the upper and lower punches 53 and 54. As shown on the right side of the figure, the bearing is inserted into the sleeve 20 and joined together, and at the same time, the upper and lower bearing surfaces are finished to a predetermined size and coaxiality to obtain a desired composite bearing. Insertion refers to insertion by press-fitting or caulking, and is sometimes simply referred to as press-fitting. In addition, it is natural that the lubricating oil is impregnated before or after the insertion operation.
In this composite bearing, the sleeve member is suitably a ferrous sintered alloy for mechanical parts with high rigidity, and the bearing member has a pore diameter smaller than that of the sleeve member and is baked for ferrous or bronze oil-impregnated bearings. It is selected according to the required specifications from gold. An intermediate portion of bearing members at both ends (hereinafter sometimes simply referred to as “bearings”), and a gap between the shaft and the inner surface of the sleeve when the rotary shaft is mounted functions as a clearance portion 42 with respect to sliding between the bearing and the shaft.

この複合軸受は機器のハウジング内に圧入・固定して用いられるが、スリーブ２０の材質が機械部品用の焼結合金で剛性が高いために圧入時に軸受面や同軸度に狂いを生じることはなく、そのまま使用に供することができる。また、スリーブが多孔質なので全休の含油量が多く、さらに運転に伴い（熱膨張して軸受から）滲み出た潤滑油は逃げ部からスリーブに吸収され、（運転休止時にスリーブより気孔径が小さい焼結軸受に毛細管力で吸引されて）再び軸受に循環するため、これらの作用が相俟って軸受寿命が長くなる。   This composite bearing is used by being press-fitted and fixed in the housing of the equipment. However, since the material of the sleeve 20 is a sintered alloy for machine parts and has high rigidity, there will be no deviation in the bearing surface and coaxiality during press-fitting. Can be used as is. Also, since the sleeve is porous, the oil content during all holidays is high, and the lubricating oil that oozes out from the bearing (due to thermal expansion) is absorbed into the sleeve from the escape portion and has a smaller pore diameter than the sleeve when the operation is suspended. Since these are circulated again to the bearing (sucked by the capillary force into the sintered bearing), the combined action of these increases the bearing life.

逃げ部４２における軸とスリーブ内面の間隔については、回転軸の振れに対する逃げという観点からは接触を生じない限り任意であるが、滲み出た潤滑油の一時貯留〜スリーブへの吸収という観点からは、間隔が大きすぎるとスリーブへの回収が円滑に行えなくなるため、間隔の上限は５ｍｍまで、好ましくは３ｍｍ以下とする。一方、スリーブの内面がストレートの場合に、この値が小さいと、軸受の肉厚も小さくなるため、軸受の製造や品質面での制約を受ける。従って、この場合は１ｍｍを間隔の下限値とする。   About the space | interval of the axis | shaft in the escape part 42, and a sleeve inner surface, from the viewpoint of escape with respect to the shake | fluctuation of a rotating shaft, as long as it does not produce contact, If the interval is too large, recovery to the sleeve cannot be performed smoothly. Therefore, the upper limit of the interval is set to 5 mm, preferably 3 mm or less. On the other hand, when the inner surface of the sleeve is straight, if this value is small, the thickness of the bearing also becomes small, which is subject to restrictions on the production and quality of the bearing. Therefore, in this case, 1 mm is set as the lower limit of the interval.

一方、軸受部材の端面側に滲み出した潤滑油の回収を図るためには、スリーブの端面を軸受部材の端面よりも高く設定する。滲み出した潤滑油や回転軸を伝って漏れる潤滑油は軸受端面に近接して回転軸に固定された油留め輪によって振り切られ飛散するが、これをスリーブの内壁面で受け止めて多孔質のスリーブ内に吸収し、軸受部材に循環させる訳である。またこの場合、スリーブ両端部の内壁面を中心軸に対する角度１０〜３０°のテーパー面（円錐面）に形成しておくとこのテーパー部が油溜りとなり、滲み出した潤滑油の回収が一層容易になる。角度が広すぎると油溜りの作用が劣り、狭すぎるとテーパー面と油留め輪の間隔がなくなり何れも好ましくない。このテーパーは、軸受部材をスリーブに圧入する際のガイドにもなり、また、この部分はパンチと接触せずに済むためにパンチの抜き出しも容易になり、再圧作業の円滑化に役立つものである。   On the other hand, in order to collect the lubricating oil that has oozed out to the end face side of the bearing member, the end face of the sleeve is set higher than the end face of the bearing member. Exuded lubricating oil or lubricating oil leaking along the rotating shaft is sprinkled off and scattered by an oil retaining ring fixed to the rotating shaft in the vicinity of the bearing end surface, but this is received by the inner wall surface of the sleeve and is a porous sleeve It is absorbed inside and circulated through the bearing member. In this case, if the inner wall surfaces of both end portions of the sleeve are formed on a tapered surface (conical surface) having an angle of 10 to 30 ° with respect to the central axis, the tapered portion becomes an oil reservoir, and it is easier to collect the exuded lubricating oil. become. If the angle is too wide, the action of the oil sump is inferior. If it is too narrow, there is no gap between the tapered surface and the oil retaining ring, which is not preferable. This taper also serves as a guide when the bearing member is press-fitted into the sleeve, and since this part does not need to contact the punch, the punch can be easily pulled out, which helps smooth the re-pressing operation. is there.

本発明の複合軸受にあっては、その外周を形成するスリーブの剛性が高いので、機器のハウジングに圧入・固定する際に両端部の軸受面やその同軸度が狂う虞がなく、そのまま使用に供することができる。また、スリーブが多孔質なので全体の含油量が多く、運転に伴い滲み出た潤滑油は逃げ部からスリーブに吸収されて再び軸受に循環し、軸受の端面側に滲み出した潤滑油もスリーブの内壁面で吸収されるため、これらの作用が相俟って軸受の寿命を延長することができる。   In the composite bearing of the present invention, since the sleeve forming the outer periphery thereof is highly rigid, there is no possibility that the bearing surfaces at both ends and the coaxiality thereof will be out of order when being press-fitted and fixed to the housing of the device, and can be used as it is. Can be provided. In addition, since the sleeve is porous, the total oil content is high.Lubricated oil that oozes out during operation is absorbed by the sleeve from the escape portion and circulates again to the bearing. Since they are absorbed by the inner wall surface, these actions can be combined to extend the life of the bearing.

図１は本発明に係る複合軸受の基本的な態様を示すもので、軸受部材１０およびスリーブ２０はともに単純な直円筒形であり、軸受部材は組成が質量基準で、銅：１６〜２４％、錫：１.６〜２.４％および鉄：残部、焼結密度６.０ｇ／ｃｍ３、平均気孔径が１０μｍの含油軸受用焼結合金で作られ、スリーブは銅：１〜２％、炭素：０.７〜１％および鉄：残部、焼結密度６.４ｇ／ｃｍ３、平均気孔径が１００μｍの機械部品用焼結合金で作られている。
スリーブ２０の両端部内壁面２１は角度１５°のテーパー面に形成してある。この複合軸受はスリーブ２０と軸受部材を前記の固定方法（図２）の要領で一体化して形成され、軸受部材１０の端面をスリーブ２０の端面より深い位置まで圧入して、軸受部材の端面に近接して回転軸３０に固定された油留め輪３１によって振り切られる潤滑油をスリーブ２０のテーパー面２１で受け止めて吸収するように構成してある。なお、この実施態様におけるスリーブ２０の内面と回転軸３０との間隔が１〜５ｍｍの範囲内に設定されることは前述の通りである。 FIG. 1 shows a basic aspect of a composite bearing according to the present invention. The bearing member 10 and the sleeve 20 are both simple straight cylinders, and the composition of the bearing member is based on mass, copper: 16 to 24%. , Tin: 1.6-2.4% and iron: balance, sintered density 6.0 g / cm 3 , made of sintered bearing for oil-impregnated bearings with an average pore diameter of 10 μm, sleeve made of copper: 1-2% , Carbon: 0.7 to 1% and iron: balance, sintered density of 6.4 g / cm 3 , and average pore diameter of 100 μm.
The inner wall surfaces 21 at both ends of the sleeve 20 are formed as tapered surfaces having an angle of 15 °. This composite bearing is formed by integrating the sleeve 20 and the bearing member in the manner of the fixing method (FIG. 2), and press-fits the end face of the bearing member 10 to a position deeper than the end face of the sleeve 20 to the end face of the bearing member. The lubricating oil shaken off by the oil retaining ring 31 fixed to the rotating shaft 30 in the vicinity is received and absorbed by the tapered surface 21 of the sleeve 20. As described above, the distance between the inner surface of the sleeve 20 and the rotary shaft 30 in this embodiment is set in the range of 1 to 5 mm.

次に、図１の複合軸受における軸受部材１０の形状を鍔付き形状に変更した実施態様を図３に示す。この態様はスリーブ２０の内径側端部に、軸受部材の鍔部１１に対応する段差部２２を設け、段差部の外縁からテーパー面２１を立ち上がらせたものである。この態様においては軸受部材の圧入深さが段差部２２によって一定になり、従って上・下の両軸受部材の間隔が一定に保たれるので、複合軸受をバラツキなく量産することができる。   Next, the embodiment which changed the shape of the bearing member 10 in the compound bearing of FIG. 1 into the shape with a hook is shown in FIG. In this embodiment, a step portion 22 corresponding to the flange portion 11 of the bearing member is provided at the inner diameter side end portion of the sleeve 20, and the tapered surface 21 is raised from the outer edge of the step portion. In this embodiment, the press-fitting depth of the bearing member is made constant by the step portion 22, and the distance between the upper and lower bearing members is kept constant, so that the composite bearing can be mass-produced without variation.

次に、図１におけるスリーブ２０の内面を、中間に小径部２３のある段付き形状に変更した実施態様を図４に示す。この態様の場合、軸受部材１０の圧入深さが小径部２３の段部によって一定に保たれること、および、それに伴う利点は図３の態様の場合と同様である。
図１の態様の場合は中間の逃げ部（回転軸とスリーブ内面との空隙）が軸受部材の肉厚と一致することによる制約があったが、図４の態様の場合はスリーブ内面の小径部２３と回転軸の空隙が逃げ部となるため、その（特に下限値の）設定に際して軸受部材の肉厚を考慮する必要がなくなる。但し、この空隙が縮小（小径部の内面が回転軸に近接）するにつれて、軸受から滲み出てこの空隙に充満する潤滑油の粘性抵抗が増し、軸を駆動するモーターの消費電流を増加させる。そこでこのロスを避けるため、図４（および次の図５）の態様においては、スリーブ内面の小径部と回転軸との空隙を０.５ｍｍ以上に設定することが好ましい。 Next, FIG. 4 shows an embodiment in which the inner surface of the sleeve 20 in FIG. 1 is changed to a stepped shape having a small diameter portion 23 in the middle. In the case of this aspect, the press-fitting depth of the bearing member 10 is kept constant by the step portion of the small diameter portion 23, and the advantages associated therewith are the same as in the case of the aspect of FIG.
In the case of the embodiment of FIG. 1, there is a restriction due to the fact that the intermediate relief portion (the gap between the rotating shaft and the sleeve inner surface) matches the thickness of the bearing member, but in the case of the embodiment of FIG. Since the gap between the rotary shaft 23 and the rotary shaft serves as a relief portion, it is not necessary to consider the thickness of the bearing member when setting (particularly the lower limit value). However, as the gap is reduced (the inner surface of the small diameter portion is close to the rotating shaft), the viscous resistance of the lubricating oil that oozes out from the bearing and fills the gap increases, increasing the current consumption of the motor that drives the shaft. Therefore, in order to avoid this loss, in the embodiment of FIG. 4 (and the next FIG. 5), it is preferable to set the gap between the small diameter portion of the sleeve inner surface and the rotating shaft to 0.5 mm or more.

次に、図３におけるスリーブの内面を、中間に小径部２３のある段付き形状に変更した実施態様を図５に示す。この態様は、スリーブの内径側には両端の段差部２２、中間の小径部２３による段差の、都合２段の段差部がある場合の例で、軸受部材の鍔部１１がスリーブ両端の段差部２２によって位置決めされた状態で、スリーブの小径部２３の段部と軸受部材１０の端面との間に０.５ｍｍ以上の隙間を保つように設定した態様である。この場合、軸受端部が露出するため潤滑油の吸収が直接行えるようになる。
なお、図４および図５の態様におけるスリーブ内面の小径部２３を型出し成形する代わりに、同じ位置に、軸受部材より気孔径の大きい焼結合金からなるカラー部材を挿入・固定しても同様の効果が得られる。 Next, FIG. 5 shows an embodiment in which the inner surface of the sleeve in FIG. 3 is changed to a stepped shape having a small diameter portion 23 in the middle. This embodiment is an example in which there are two stepped portions on the inner diameter side of the sleeve, such as a stepped portion at both ends and a stepped portion at the middle small diameter portion 23. The flange portion 11 of the bearing member is a stepped portion at both ends of the sleeve. In this state, a gap of 0.5 mm or more is maintained between the step portion of the small diameter portion 23 of the sleeve and the end surface of the bearing member 10 in a state where the sleeve 22 is positioned. In this case, since the bearing end is exposed, the lubricating oil can be directly absorbed.
4 and 5, instead of molding the small diameter portion 23 on the inner surface of the sleeve, a collar member made of a sintered alloy having a pore diameter larger than that of the bearing member is inserted and fixed at the same position. The effect is obtained.

本発明の複合軸受の基本的構造を示す縦断面図である。It is a longitudinal cross-sectional view which shows the basic structure of the compound bearing of this invention. 軸受部材とスリーブとの固定手段の一例を説明する略示縦断面図である。It is a schematic longitudinal cross-sectional view explaining an example of the fixing means of a bearing member and a sleeve. 本発明に係る複合軸受の、図１と異なる態様を示す縦断面図である。It is a longitudinal cross-sectional view which shows the aspect different from FIG. 1 of the compound bearing which concerns on this invention. 本発明に係る複合軸受の、他の実施態様を示す縦断面図である。It is a longitudinal cross-sectional view which shows the other embodiment of the compound bearing which concerns on this invention. 本発明に係る複合軸受の、他の実施態様を示す縦断面図である。It is a longitudinal cross-sectional view which shows the other embodiment of the compound bearing which concerns on this invention. 特許文献１に係る軸受の概略を示す縦断面図である。It is a longitudinal cross-sectional view which shows the outline of the bearing which concerns on patent document 1. 特許文献２に係る軸受の概略を示す縦断面図である。It is a longitudinal cross-sectional view which shows the outline of the bearing which concerns on patent document 2.

符号の説明Explanation of symbols

１０ 軸受部材
１１ 鍔部
２０ スリーブ
２１ テーパー面
２２ 段差部
２３ 小径部
３０ 回転軸
３１ 油留め輪
４０ 上側の軸受
４１ 下側の軸受
４２ 逃げ部
５１ 再圧用押型
５２ コアロッド
５３ 上パンチ
５４ 下パンチ
６１ 段付き圧粉体
６２ 鋼管
６３ 上側の軸受部材
６４ 下側の軸受部材
DESCRIPTION OF SYMBOLS 10 Bearing member 11 Grow part 20 Sleeve 21 Tapered surface 22 Step part 23 Small diameter part 30 Rotating shaft 31 Oil retaining ring 40 Upper bearing 41 Lower bearing 42 Relief part 51 Repressing die 52 Core rod 53 Upper punch 54 Lower punch 61 Step Powder compact 62 Steel pipe 63 Upper bearing member 64 Lower bearing member

Claims (7)

機械部品用焼結合金からなるスリーブ（２０）の内径面両端部に、
スリーブよりも気孔径の小さい含油軸受用焼結合金からなり潤滑油を含有する軸受部材（１０）が、
一体に嵌入固定された複合焼結軸受であって、
スリーブ両端部の内壁面が中心軸に対する角度１０〜３０°のテーパー面（２１）に形成され、
軸受部材の端面がスリーブの端面よりも深く嵌入されていることを特徴とする複合焼結軸受。 At both ends of the inner diameter surface of the sleeve (20) made of a sintered alloy for machine parts ,
Bearing member containing lubricant consists small oil-impregnated sintered alloy bearing having pore diameters than the sleeves (10),
A composite sintered bearing which is fixedly fitted to one body,
The inner wall surface of the sleeves at both ends is formed in a tapered surface of angle 10 to 30 ° (21) with respect to the central axis,
Composite sintered bearing end surface of the shaft receiving member is characterized in that it is deeply inserted from the end face of the sleeve. スリーブ両端に固定された軸受部材の間の空間（逃げ部）におけるスリーブと回転軸との間隔が１〜５ｍｍである、請求項１に記載の複合焼結軸受。   The composite sintered bearing according to claim 1, wherein a space between the sleeve and the rotating shaft in a space (relief portion) between bearing members fixed to both ends of the sleeve is 1 to 5 mm. 軸受部材が鍔部（１１）を有する鍔付き形状であり、スリーブの内径側端部に軸受部材の鍔部に対応する段差部（２２）を具え、スリーブに嵌入された軸受部材がこの段差部によって位置決めされている、請求項１または請求項２に記載の複合焼結軸受。   The bearing member has a flange shape having a flange portion (11), and has a step portion (22) corresponding to the flange portion of the bearing member at the inner diameter side end portion of the sleeve, and the bearing member fitted into the sleeve is the step portion. The composite sintered bearing according to claim 1, wherein the composite sintered bearing is positioned by the following. スリーブの内径面が中間に小径部（２３）を有する段付き形状であり、スリーブに嵌入された直円筒状の軸受部材がこの小径部の端面によって位置決めされ、この小径部と回転軸との空隙が０.５ｍｍ以上である、請求項１または請求項２に記載の複合焼結軸受。   The inner diameter surface of the sleeve has a stepped shape having a small diameter portion (23) in the middle, and a straight cylindrical bearing member fitted in the sleeve is positioned by the end surface of the small diameter portion, and the gap between the small diameter portion and the rotating shaft The composite sintered bearing according to claim 1 or 2, wherein is 0.5 mm or more. 軸受部材が鍔部（１１）を有する鍔付き形状であり、スリーブの内径面がその両端に軸受部材の鍔部に対応する段差部（２２）を、中間に小径部（２３）を有する段付き形状であり、スリーブに固定される鍔付きの軸受部材が段差部（２２）によって位置決めされ、小径部（２３）と回転軸との空隙が０.５ｍｍ以上、小径部（２３）の端面と軸受部材の端面との空隙が０.５ｍｍ以上である、請求項１、請求項２および請求項３のいずれかに記載の複合焼結軸受。   The bearing member has a flange shape having a flange portion (11), the inner diameter surface of the sleeve has a stepped portion (22) corresponding to the flange portion of the bearing member at both ends thereof, and a stepped portion having a small diameter portion (23) in the middle. A flanged bearing member that is shaped and fixed to the sleeve is positioned by the stepped portion (22), the gap between the small diameter portion (23) and the rotating shaft is 0.5 mm or more, and the end surface of the small diameter portion (23) and the bearing The composite sintered bearing according to any one of claims 1, 2, and 3, wherein a gap with an end face of the member is 0.5 mm or more. スリーブ内面に型出し成形される小径部（２３）に代えて、同じ位置に軸受部材よりも気孔径の大きい焼結合金からなるカラー部材を挿入・固定した請求項４または請求項５に記載の複合焼結軸受。   The collar member according to claim 4 or 5, wherein a collar member made of a sintered alloy having a pore diameter larger than that of the bearing member is inserted and fixed at the same position in place of the small diameter portion (23) formed by molding on the inner surface of the sleeve. Composite sintered bearing. 軸受部材の端面に近接して回転軸に固定される油留め輪（３１）の位置が、スリーブの端面よりも深く設定された請求項１から請求項６のいずれかに記載の複合焼結軸受。
The composite sintered bearing according to any one of claims 1 to 6, wherein the position of the oil retaining ring (31) fixed to the rotating shaft in the vicinity of the end face of the bearing member is set deeper than the end face of the sleeve. .
JP2004222844A 2004-07-30 2004-07-30 Composite sintered bearing Expired - Fee Related JP4448401B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2004222844A JP4448401B2 (en) 2004-07-30 2004-07-30 Composite sintered bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2004222844A JP4448401B2 (en) 2004-07-30 2004-07-30 Composite sintered bearing

Publications (2)

Publication Number Publication Date
JP2006038185A JP2006038185A (en) 2006-02-09
JP4448401B2 true JP4448401B2 (en) 2010-04-07

Family

ID=35903377

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2004222844A Expired - Fee Related JP4448401B2 (en) 2004-07-30 2004-07-30 Composite sintered bearing

Country Status (1)

Country Link
JP (1) JP4448401B2 (en)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4675880B2 (en) * 2006-12-27 2011-04-27 Ｎｔｎ株式会社 Method for manufacturing fluid dynamic bearing device
KR101044101B1 (en) 2010-01-11 2011-06-28 삼성전기주식회사 Brushless dc motor
CN102223005A (en) * 2010-04-13 2011-10-19 德昌电机(深圳)有限公司 Rotor bearing arrangement
JP2012036824A (en) * 2010-08-06 2012-02-23 Daikin Industries Ltd Bearing housing
JP2012067652A (en) * 2010-09-22 2012-04-05 Kubota Corp Sealing device of rotary part of engine
JP2013194753A (en) * 2012-03-15 2013-09-30 Taiho Kogyo Co Ltd Sliding member and method of manufacturing the sliding member
CN104246251B (en) * 2012-03-30 2017-05-17 大丰工业株式会社 Sliding member and method for manufacturing sliding member
KR102648545B1 (en) * 2016-07-19 2024-03-18 엘지이노텍 주식회사 Fan motor and vehicle having the same

Also Published As

Publication number Publication date
JP2006038185A (en) 2006-02-09

Similar Documents

Publication Publication Date Title
US6105250A (en) Method of producing hydrodynamic type porous oil-impregnated bearing
JP4448401B2 (en) Composite sintered bearing
JP6199106B2 (en) Sintered bearing, method for manufacturing the same, and fluid dynamic bearing device provided with the sintered bearing
JP2014001781A (en) Fluid dynamic pressure bearing device and motor including the same
CN107781293B (en) Dynamic pressure bearing, method of manufacturing the same, fluid dynamic pressure bearing device, motor, and molding die
JP2008002650A (en) Dynamic-pressure bearing unit, its manufacturing method, and spindle motor
JP3770578B2 (en) Method for producing sintered oil-impregnated bearing
JP4573349B2 (en) Manufacturing method of hydrodynamic bearing
JP2006316896A (en) Method for manufacturing oil-impregnated sintered bearing and oil-impregnated sintered bearing
JP3607478B2 (en) Dynamic pressure type porous oil-impregnated bearing
WO2017159345A1 (en) Dynamic pressure bearing and method for manufacturing same
JP2008267394A (en) Method of manufacturing bearing unit
JP3818626B2 (en) Method for producing sintered oil-impregnated bearing
US11428266B2 (en) Slide bearing
JP4188288B2 (en) Manufacturing method of dynamic pressure type porous oil-impregnated bearing
JP4327038B2 (en) Spindle motor
JP6449059B2 (en) Sintered oil-impregnated bearing and manufacturing method thereof
JP3698352B2 (en) Manufacturing method of bearing
WO2023189389A1 (en) Oil-impregnated sintered bearing and fluid dynamic bearing device including same
JP2016180496A (en) Bearing member and manufacturing method thereof
WO2016152474A1 (en) Bearing member, fluid dynamic pressure bearing device equipped with same, and method of manufacturing bearing member
JP3856363B2 (en) Manufacturing method of bearing
JP2021001629A (en) Bearing member and fluid dynamic pressure bearing device including the same
JP2005180707A (en) Dynamic pressure type sintered oil-impregnated bearing unit
JP2004340385A (en) Dynamic pressure type bearing unit

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20070511

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20090901

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20091117

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20091211

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20100119

A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20100122

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130129

Year of fee payment: 3

R150 Certificate of patent or registration of utility model

Free format text: JAPANESE INTERMEDIATE CODE: R150

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130129

Year of fee payment: 3

S111 Request for change of ownership or part of ownership

Free format text: JAPANESE INTERMEDIATE CODE: R313111

R350 Written notification of registration of transfer

Free format text: JAPANESE INTERMEDIATE CODE: R350

LAPS Cancellation because of no payment of annual fees