JPS5851456Y2 - cardan joint bearing - Google Patents

cardan joint bearing

Info

Publication number
JPS5851456Y2
JPS5851456Y2 JP1979107816U JP10781679U JPS5851456Y2 JP S5851456 Y2 JPS5851456 Y2 JP S5851456Y2 JP 1979107816 U JP1979107816 U JP 1979107816U JP 10781679 U JP10781679 U JP 10781679U JP S5851456 Y2 JPS5851456 Y2 JP S5851456Y2
Authority
JP
Japan
Prior art keywords
shell case
cardan joint
spider shaft
center
joint 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
Application number
JP1979107816U
Other languages
Japanese (ja)
Other versions
JPS5625828U (en
Inventor
康宏 藤井
Original Assignee
光洋精工株式会社
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 光洋精工株式会社 filed Critical 光洋精工株式会社
Priority to JP1979107816U priority Critical patent/JPS5851456Y2/en
Publication of JPS5625828U publication Critical patent/JPS5625828U/ja
Application granted granted Critical
Publication of JPS5851456Y2 publication Critical patent/JPS5851456Y2/en
Expired legal-status Critical Current

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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C21/00—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
    • F16C21/005—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement the external zone of a bearing with rolling members, e.g. needles, being cup-shaped, with or without a separate thrust-bearing disc or ring, e.g. for universal joints
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/08—Sliding-contact bearings for exclusively rotary movement for axial load only for supporting the end face of a shaft or other member, e.g. footstep bearings
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
    • F16D3/38—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another
    • F16D3/382—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another constructional details of other than the intermediate member
    • F16D3/385—Bearing cup; Bearing construction; Bearing seal; Mounting of bearing on the intermediate member
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/41—Couplings
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
    • F16D3/38—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another
    • F16D3/40—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another with intermediate member provided with two pairs of outwardly-directed trunnions on intersecting axes
    • F16D3/41—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another with intermediate member provided with two pairs of outwardly-directed trunnions on intersecting axes with ball or roller bearings

Description

【考案の詳細な説明】 本考案はシェルケースの底部でスパイダー軸の端面を支
え、かつ前記シェルケースの円筒部内周面に配設した針
状ころで前記スパイダー軸の外周面を支持したカルダン
継手の軸受に関する。[Detailed description of the invention] The present invention is a Cardan joint in which the end face of the spider shaft is supported at the bottom of a shell case, and the outer peripheral surface of the spider shaft is supported by needle rollers arranged on the inner peripheral surface of the cylindrical part of the shell case. Regarding bearings.

通常この種のカルダン継手の軸受は、薄鋼板を絞り加工
して成形したシェルケースを、該シェルケースの底部と
スパイダー軸の端面との間に予圧が作用するようにカル
ダン継手のヨークの軸受孔に組み込み、前記カルダン継
手のスパイダー軸の軸方向のガタを防止しているが、軸
受固定位置の誤差等により予圧量が変化しやすく、予圧
が過大になった場合にはカルダン継手の折曲げ抵抗トル
クが増加したり、あるいはシェルケースの内面とスパイ
ダー軸端面との間で焼付が発生したりし、逆に予圧が小
さければ衝撃等を受けた際、すぐに予圧が抜けてしまい
ガタが発生するという不都合が生じている。Normally, this type of cardan joint bearing is made of a shell case made by drawing a thin steel plate, and the bearing hole of the yoke of the cardan joint is made such that a preload acts between the bottom of the shell case and the end face of the spider shaft. This prevents the axial play of the spider shaft of the Cardan joint, but the amount of preload is likely to change due to errors in the bearing fixing position, and if the preload becomes excessive, the bending resistance of the Cardan joint will increase. Torque may increase, or seizure may occur between the inner surface of the shell case and the end face of the spider shaft.On the other hand, if the preload is small, the preload will be quickly lost when it receives an impact, causing play. This is an inconvenience.

そのため軸受固定後にハンマリング等により予圧微調整
を行っているが正確な予圧量が得られに＜＜、また工数
も非常にかかつている。For this reason, after the bearing is fixed, the preload is finely adjusted by hammering or the like, but it is difficult to obtain an accurate amount of preload, and it also takes a lot of man-hours.

本考案の目的はこの予圧微調整が正確かつ容易に行える
カルダン継手の軸受を提供するにある。The object of the present invention is to provide a cardan joint bearing that allows fine preload adjustment to be made accurately and easily.

以下実施例に基づき本考案を説明する。The present invention will be explained below based on examples.

第１図は本考案の実施例を示す縦断面図であって、１は
薄鋼板を絞り加工して成形したシェルケースである。FIG. 1 is a longitudinal sectional view showing an embodiment of the present invention, and 1 is a shell case formed by drawing a thin steel plate.

該シェルケース１はその円筒部内周面に配設した針状こ
ろ２でスパイダー軸３の外周面を回動自在に支持し、か
つ前記シェルケース１の底部１０の内面１２で前記スパ
イダー軸３の端面３１中央を支持するようにカルダン継
手のヨーク４の軸受孔５に嵌入され、図示しない工具に
より前記軸受孔５の内周壁の数箇所を塑性変形して、シ
ェルケース１の底部周縁部１３上に突出させた突起６で
、シェルケース１とスパイダー軸３の間に予圧が作用す
るように軸方向に固定される。The shell case 1 rotatably supports the outer circumferential surface of the spider shaft 3 with needle rollers 2 disposed on the inner circumferential surface of its cylindrical portion, and the inner surface 12 of the bottom 10 of the shell case 1 supports the spider shaft 3. It is inserted into the bearing hole 5 of the yoke 4 of the cardan joint so as to support the center of the end surface 31, and by plastically deforming several places on the inner peripheral wall of the bearing hole 5 using a tool (not shown), the top of the bottom peripheral edge 13 of the shell case 1 is inserted. The shell case 1 and the spider shaft 3 are fixed in the axial direction by a protrusion 6 that projects so that a preload is applied between the shell case 1 and the spider shaft 3.

シェルケース１の底部１０は、ケース１の内方にスパイ
ダー軸端面３１の中央を支える尖端面１２ａを有し底部
中央に向って順次肉厚を増加する断面略円すい台形状に
形成すると共に、底部１０の外面１１に円形の凹み１４
を設けて底部外周縁部１３の近傍の底部肉厚を比較的薄
くする。The bottom part 10 of the shell case 1 has a pointed end face 12a that supports the center of the spider shaft end face 31 inside the case 1, and is formed into a substantially trapezoidal cross-section with a wall thickness that gradually increases toward the center of the bottom part. A circular recess 14 on the outer surface 11 of 10
is provided to make the bottom wall thickness near the bottom outer peripheral edge 13 relatively thin.

したがってシェルケース１の底部１０の内面１２は、中
央に形成された尖端面１２ａのみをスパイダー軸端面３
１に接触させて同端面３１を支持する。Therefore, the inner surface 12 of the bottom part 10 of the shell case 1 has only the pointed end surface 12a formed in the center connected to the spider shaft end surface 3.
1 and supports the same end surface 31.

また、前記シェルケース１の底部内面１２に第２図及び
第３図に示すように該内面１２の中心部から放射状に底
部周縁部１３に向かって油溝１５を十字形に形成すれば
、シェルケース内底面１２とスパイダー軸端面３１との
接触面における潤滑を円滑にできる。Further, if the oil grooves 15 are formed in the shape of a cross in the bottom inner surface 12 of the shell case 1 radially from the center of the inner surface 12 toward the bottom peripheral edge 13 as shown in FIGS. Smooth lubrication can be achieved at the contact surface between the case inner bottom surface 12 and the spider shaft end surface 31.

なお、実施例では前記油溝１５を十字形に形成した力入
これに限定されることなく、必要に応じて溝数を増減さ
せてもよいことはもちろんであり、少なくともシェルケ
ースの底部内面１２の中心部から底部周縁部１３に向か
って放射状に形成してあればよいものである。In the embodiment, the oil grooves 15 are formed in a cross shape, but the number of grooves may be increased or decreased as necessary. It suffices if they are formed radially from the center toward the bottom peripheral edge 13.

本考案は以上の構成であってシェルケース底部１０の周
縁部１３の肉厚を比較的薄くして該周縁部１３の剛性を
低下させ、かつシェルケース底部内面１２の中央部に形
成された尖端面１２ａのみで、スパイダー軸端面３１を
支持するようにしたので、前記両端面１２ａ、３１に予
圧を作用させた時、シェルケース底部１０基体を前記周
縁部１３を支点としてたわみやすくすることができる。The present invention has the above-mentioned configuration, in which the wall thickness of the peripheral edge 13 of the shell case bottom 10 is made relatively thin to reduce the rigidity of the peripheral edge 13, and a pointed tip is formed in the center of the inner surface 12 of the shell case bottom. Since the spider shaft end surface 31 is supported only by the surface 12a, when a preload is applied to the both end surfaces 12a, 31, the base of the shell case bottom 10 can be easily bent about the peripheral edge 13 as a fulcrum. .

すなわちシェルケース底部１０全体のバネ定数を小さく
できるので、該シェルケース底部１０のたわみ量に対し
、前記両端面間における予圧荷重の変化を小さくでき、
従ってヨーク４の軸受孔５内への軸受固定時に生ずるシ
ェルケース１の軸方向固定位置のばらつきや、カルダン
継手使用時に衝撃等によるガタが発生しても、シェルケ
ース底部１０とスパイダー軸端面３１との間には常に一
定の予圧が作用し、予圧増加や予圧抜けを防止できる。That is, since the spring constant of the entire shell case bottom 10 can be made small, the change in preload load between the two end faces can be made small with respect to the amount of deflection of the shell case bottom 10.
Therefore, even if there is variation in the axial fixing position of the shell case 1 that occurs when the bearing is fixed in the bearing hole 5 of the yoke 4, or if play occurs due to impact or the like when using a cardan joint, the shell case bottom 10 and the spider shaft end surface 31 may A constant preload always acts between the two, and it is possible to prevent an increase in preload or a loss of preload.

またシェルケース底部１０の円すい面１２ｂの勾配を変
えてシェルケース底部１０の周縁部１３の肉厚を調整す
ることにより、前記シェルケース底部１０全体のバネ定
数を任意に決定できるので軸受の予圧量調整も容易にか
つ正確に行える。In addition, by changing the slope of the conical surface 12b of the shell case bottom 10 and adjusting the wall thickness of the peripheral edge 13 of the shell case bottom 10, the spring constant of the entire shell case bottom 10 can be arbitrarily determined. Adjustments can also be made easily and accurately.

さらにスパイダー軸端面には底部内面１２の中央部に形
成した尖端面１２ａのみが接触するため回転抵抗が小さ
くなり、カルダン継手の折曲げ抵抗トルクが低減できる
。Further, since only the pointed end surface 12a formed at the center of the bottom inner surface 12 contacts the end surface of the spider shaft, the rotational resistance is reduced, and the bending resistance torque of the Cardan joint can be reduced.

またシェルケース底部１０の中央部の肉厚が大きくなる
ので油溝１４を深く形成でき、グリース保有量が増加し
、かつグリース循環が円滑に行え潤滑性能が向上する。Further, since the wall thickness of the central portion of the shell case bottom 10 is increased, the oil groove 14 can be formed deeply, the amount of grease retained is increased, and the grease circulation can be performed smoothly, thereby improving the lubrication performance.

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

第１図は本考案の実施例を示す縦断面図、第２図は本考
案の他の実施例を示す縦断面、第３図は第２図における
山−■線断面図である。 １・・・・・・シェルケース、２・・・・・・針状ころ
、３・・・・・・スパイダー軸、４・・・・・・ヨーク
、５・・・・・・軸受孔、６・・・・・・突起、１０・
・・・・・底部、１１・・・・・・外面、１２・・・・
・・内面、１３・・・・・・周縁部、１４・・・・・佃
み、１５・・・・・・油溝、１２ａ・・・・・・尖端面
。FIG. 1 is a longitudinal cross-sectional view showing an embodiment of the present invention, FIG. 2 is a longitudinal cross-sectional view showing another embodiment of the present invention, and FIG. 3 is a cross-sectional view taken along the line - 2 in FIG. 1...Shell case, 2...Needle roller, 3...Spider shaft, 4...Yoke, 5...Bearing hole, 6... Protrusion, 10.
...Bottom, 11...Outer surface, 12...
...Inner surface, 13...Periphery, 14...Tsukudashi, 15...Oil groove, 12a...Point end surface.

Claims (2)

【実用新案登録請求の範囲】[Scope of utility model registration request] （１）シェルケースの底部でスパイダー軸の端面を支え
、かつ前記シェルケースの円筒部内周面に配設した針状
ころで前記スパイダー軸の外周面を支持したカルダン継
手の軸受において、シェルケースの底部を、ケース内方
にスパイダー軸端面中央を支える尖端面を有し、底部中
央に向って順次肉厚を増加する断面略円すい台形状に形
成すると共に、底部外面に凹みを設けて底部外周縁部の
近傍の底部肉厚を比較的薄くしたことを特徴とするカル
ダン継手の軸受。(1) In a cardan joint bearing in which the end surface of the spider shaft is supported at the bottom of the shell case, and the outer circumferential surface of the spider shaft is supported by needle rollers arranged on the inner circumferential surface of the cylindrical portion of the shell case, The bottom has a pointed end surface that supports the center of the spider shaft end surface inside the case, and is formed into a generally trapezoidal cross-section with a wall thickness that gradually increases toward the center of the bottom. A cardan joint bearing characterized by having a relatively thin bottom wall near the bottom. （２）前記カルダン継手のシェルケースの底部内面に、
中心部から放射状に溝を形成したことを特徴とする実用
新案登録請求の範囲第１項記載のカルダン継手の軸受。(2) On the bottom inner surface of the shell case of the cardan joint,
A cardan joint bearing according to claim 1, characterized in that grooves are formed radially from the center.
JP1979107816U 1979-08-03 1979-08-03 cardan joint bearing Expired JPS5851456Y2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP1979107816U JPS5851456Y2 (en) 1979-08-03 1979-08-03 cardan joint bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP1979107816U JPS5851456Y2 (en) 1979-08-03 1979-08-03 cardan joint bearing

Publications (2)

Publication Number Publication Date
JPS5625828U JPS5625828U (en) 1981-03-10
JPS5851456Y2 true JPS5851456Y2 (en) 1983-11-24

Family

ID=29340428

Family Applications (1)

Application Number Title Priority Date Filing Date
JP1979107816U Expired JPS5851456Y2 (en) 1979-08-03 1979-08-03 cardan joint bearing

Country Status (1)

Country Link
JP (1) JPS5851456Y2 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63216684A (en) * 1987-03-06 1988-09-08 マックス株式会社 Box nailing machine
JP6354351B2 (en) * 2014-06-05 2018-07-11 日本精工株式会社 Bearing cup for cross shaft universal joint, manufacturing method thereof, and cross shaft universal joint

Also Published As

Publication number Publication date
JPS5625828U (en) 1981-03-10

Similar Documents

Publication Publication Date Title
JP2008539369A (en) Universal joint with axial guide
JPH05157116A (en) Automatic aligning roller bearing with retainer
JPS6347930B2 (en)
JPS62274114A (en) Radial roller bearing
JPS63158316A (en) Thrust bearing
JP2008175310A (en) Thrust roller bearing cage and thrust roller bearing
EP2098738A1 (en) Thrust roller bearing
JPS5851456Y2 (en) cardan joint bearing
US7878715B2 (en) Thrust roller bearing
US6092636A (en) Oneway clutch
JPH0324891Y2 (en)
JP2015055274A (en) Thrust roller bearing, and method of manufacturing thrust roller bearing
JP2567601Y2 (en) Thrust needle bearing
JPS6011250B2 (en) How to install ball bearings
JPS6212095Y2 (en)
JPS6128121Y2 (en)
JPH0725849Y2 (en) Spindle head spindle support device
JPH062029Y2 (en) Shell needle roller bearings
JPS5911211Y2 (en) Synthetic resin cage for rolling bearings
JP2596893Y2 (en) bearing
JP2000227125A (en) Tripod type constant velocity universal joint
JPS603397Y2 (en) Shaft support device for cruciform universal joint
JPS6113772Y2 (en)
JPS5939209Y2 (en) bearing
JPH02134318U (en)