JPH0311459Y2 - - Google Patents
Info
- Publication number
- JPH0311459Y2 JPH0311459Y2 JP1983036448U JP3644883U JPH0311459Y2 JP H0311459 Y2 JPH0311459 Y2 JP H0311459Y2 JP 1983036448 U JP1983036448 U JP 1983036448U JP 3644883 U JP3644883 U JP 3644883U JP H0311459 Y2 JPH0311459 Y2 JP H0311459Y2
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- linear
- shaft body
- sliding
- grooves
- 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
Links
- 239000000314 lubricant Substances 0.000 claims description 32
- 239000004519 grease Substances 0.000 description 21
- 239000010687 lubricating oil Substances 0.000 description 20
- 239000003921 oil Substances 0.000 description 18
- 235000013290 Sagittaria latifolia Nutrition 0.000 description 6
- 235000015246 common arrowhead Nutrition 0.000 description 6
- 238000005461 lubrication Methods 0.000 description 6
- 238000005086 pumping Methods 0.000 description 4
- 238000011109 contamination Methods 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000004323 axial length Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- QNRATNLHPGXHMA-XZHTYLCXSA-N (r)-(6-ethoxyquinolin-4-yl)-[(2s,4s,5r)-5-ethyl-1-azabicyclo[2.2.2]octan-2-yl]methanol;hydrochloride Chemical compound Cl.C([C@H]([C@H](C1)CC)C2)CN1[C@@H]2[C@H](O)C1=CC=NC2=CC=C(OCC)C=C21 QNRATNLHPGXHMA-XZHTYLCXSA-N 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 239000000853 adhesive Substances 0.000 description 1
- 230000001070 adhesive effect Effects 0.000 description 1
- 239000003570 air Substances 0.000 description 1
- 229910003460 diamond Inorganic materials 0.000 description 1
- 239000010432 diamond Substances 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 229920003002 synthetic resin Polymers 0.000 description 1
- 239000000057 synthetic resin Substances 0.000 description 1
- 230000008685 targeting Effects 0.000 description 1
Landscapes
- Sliding-Contact Bearings (AREA)
- Bearings For Parts Moving Linearly (AREA)
Description
【考案の詳細な説明】
この考案は、潤滑剤を内蔵する動圧形すべり軸
受に関し、とくに、正逆両方向の直線運動、もし
くは回転直線運動が相対的に可能な軸体と軸受と
の少なくとも一方のすべり面に、矢じり状の動圧
発生用のみぞを配設し、軸受の側面に設けた潤滑
剤溜り部に、多孔性部材を介在させて潤滑油もし
くはグリースを内蔵させることにより、潤滑剤を
長期間補給せずに使用できるようにしたものであ
る。[Detailed description of the invention] This invention relates to a hydrodynamic slide bearing containing a lubricant, and in particular, at least one of the shaft body and the bearing is capable of relative linear movement in both forward and reverse directions, or rotational linear movement. An arrowhead-shaped groove for generating dynamic pressure is provided on the sliding surface of the bearing, and a porous member is inserted in the lubricant reservoir provided on the side of the bearing to contain lubricant oil or grease. This allows it to be used for long periods of time without replenishing it.
従来の動圧形ラジアルすべり軸受では、軸受の
すべり面に矢じり状の動圧発生用のみぞを設けた
ものが知られているが、軸体は軸受に対して一方
向に回転するだけで、正逆両方向に回転すること
はできない。 Conventional dynamic pressure type radial sliding bearings are known to have arrowhead-shaped grooves for generating dynamic pressure on the sliding surface of the bearing, but the shaft only rotates in one direction with respect to the bearing. It cannot be rotated in both forward and reverse directions.
そこで、この考案者らは、ラジアルすべり軸受
以外のリニアーすべり軸受、ラジアル・リニアー
すべり軸受を対象とする正逆両方向の運動が可能
な動圧形すべり軸受の考案について、さきに実用
新案登録の出願を行つた（実願昭57−128381号参
照）。該出願に係る動圧形すべり軸受は、軸体と
軸受とのすべり面の少なくとも一方に、矢じり状
の動圧発生用のみぞが形成され、該動圧発生用の
みぞは、矢先方向が軸体と軸受との一方向の運動
方向に一致するみぞと、矢先方向が他方の運動方
向に一致するみぞとからなり、これらのみぞをそ
れぞれすべり面に配列する構成としている。 Therefore, the inventors have previously applied for utility model registration for the idea of a hydrodynamic sliding bearing that can move in both forward and reverse directions, targeting linear sliding bearings other than radial sliding bearings, and radial/linear sliding bearings that can move in both forward and reverse directions. (Refer to Utility Application No. 128381, 1983). In the hydrodynamic sliding bearing according to the application, an arrowhead-shaped groove for generating dynamic pressure is formed on at least one of the sliding surfaces of the shaft body and the bearing, and the groove for generating dynamic pressure is oriented in the direction of the arrow. It consists of a groove that coincides with one direction of movement of the body and the bearing, and a groove whose arrowhead direction coincides with the other direction of movement, and these grooves are arranged on the sliding surface.
上記の軸受は、潤滑剤として潤滑剤油、グリー
ス、空気等が用いられるが、直線運動用のリニア
ーすべり軸受と回転直線運動用のラジアル・リニ
アーすべり軸受との潤滑を潤滑油またはグリース
を使用して行なう場合は、あらかじめ軸体のすべ
り面に潤滑油またはグリースを塗布するか、ある
いは軸体と軸受とのすべり面の少なくとも一方の
両端部に設けた比較的浅い環状みぞ、もしくは動
圧発生用のみぞの間に設けた比較的浅い凹部にグ
リースが封入できるようになつている。 The above bearings use lubricant oil, grease, air, etc. as a lubricant, but lubricating oil or grease is used to lubricate the linear sliding bearing for linear motion and the radial linear sliding bearing for rotational linear motion. If this is the case, apply lubricating oil or grease to the sliding surface of the shaft body in advance, or use relatively shallow annular grooves or grooves for generating dynamic pressure provided at both ends of at least one of the sliding surfaces between the shaft body and the bearing. Grease can be sealed in a relatively shallow recess provided between the grooves.
しかし、上記の潤滑法のうち、前者のように、
軸体のすべり面に潤滑油またはグリースを塗布す
る方法では、軸体もしくは軸受が正逆両方向に交
互に直線運動、あるいは回転直線運動をすると、
潤滑に必要とする油量以外の余分の潤滑油または
グリースが、軸体もしくは軸受の往復運動に伴つ
て移動してストローク長の両端部に集まり、両端
部から逐次滴下して潤滑剤保有量が漸減するた
め、油切れやグリース切れが生じ易く、軸受周辺
の機材が汚染される問題があることが判明した。 However, among the above lubrication methods, like the former,
In the method of applying lubricating oil or grease to the sliding surface of the shaft, when the shaft or bearing moves linearly in both forward and reverse directions alternately or in rotational linear motion,
Excess lubricating oil or grease other than the amount required for lubrication moves as the shaft or bearing reciprocates, collects at both ends of the stroke length, and drips from both ends sequentially, reducing the amount of lubricant retained. It was found that because the bearing gradually decreases, it tends to run out of oil and grease, which leads to contamination of equipment around the bearing.
また、後者の潤滑法のように、環状みぞや凹部
にグリースを封入する方法でも、環状みぞや凹部
の深さが浅くて封入できるグリース量には限度が
あるため、長期間使用するとグリース切れが生じ
易く前者の場合と同様の問題があるほか、潤滑油
や低粘度のグリースは封入できないという問題が
あることが明らかになつた。 In addition, even with the latter lubrication method, in which grease is sealed in an annular groove or recess, the depth of the annular groove or recess is shallow and there is a limit to the amount of grease that can be filled, so the grease may run out after long-term use. It has become clear that in addition to the same problem as the former case, which is easy to occur, there is also the problem that lubricating oil and low-viscosity grease cannot be sealed.
この考案は、正逆両方向の運動が可能な動圧形
のリニアーすべり軸受とラジアル・リニアーすべ
り軸受とにおける上記の問題を解決するためにな
されたものであり、この考案の目的は、上記動圧
形すべり軸受における潤滑剤の漏出を少なくし
て、長期間に亘つて潤滑剤の補給を不要とするこ
とにあり、また、この考案の目的は、上記動圧形
すべり軸受周辺の機材の潤滑剤漏出による汚染を
防止することにある。 This invention was made in order to solve the above-mentioned problems in hydrodynamic linear sliding bearings and radial linear sliding bearings that can move in both forward and reverse directions. The purpose of this invention is to reduce lubricant leakage from type plain bearings and eliminate the need for lubricant replenishment over a long period of time. The purpose is to prevent contamination due to leakage.
すなわち、この考案は、後述する実施例および
図面に示すように、軸体１０と軸受２０とが相互
のすべり面１１，２１を介して正逆両方向の直線
運動が相対的に可能であり、前記すべり面１１，
２１の少なくとも一方に、矢じり状の動圧発生用
のみぞ４０，５０が形成され、該動圧発生用のみ
ぞは、矢先方向が軸体１０と軸受２０との一方向
の運動方向に一致するみぞ４０と、矢先方向が他
方の運動方向に一致するみぞ５０とを、それぞれ
前記すべり面１１，２１に備え、矢先方向が一方
の運動方向に一致するみぞ４０と他方の運動方向
に一致するみぞ５０とは、いずれも軸方向の二ヶ
所以上に配列されると共に軸方向と直交する方向
の二ヶ所以上に配列された動圧形すべり軸受であ
つて、前記軸受２０の側面に設けた潤滑剤溜り部
６０に、潤滑剤を含浸させた多孔性部材６１を取
り付け、該多孔性部材６１を、軸体１０のすべり
面１１，１２に接触させたことを特徴とする潤滑
剤を内蔵する動圧形すべり軸受に係る。 That is, in this invention, as shown in the embodiments and drawings described later, the shaft body 10 and the bearing 20 are relatively capable of linear motion in both forward and reverse directions via mutual sliding surfaces 11 and 21. sliding surface 11,
Arrowhead-shaped grooves 40 and 50 for generating dynamic pressure are formed in at least one of the grooves 21, and the direction of the arrow of the groove for generating dynamic pressure coincides with the direction of movement of the shaft body 10 and the bearing 20 in one direction. A groove 40 and a groove 50 whose arrow head direction coincides with the other movement direction are provided on the sliding surfaces 11 and 21, respectively, and the groove 40 whose arrow head direction corresponds to one movement direction and the groove 50 whose arrow head direction corresponds to the other movement direction. Reference numeral 50 refers to a hydrodynamic sliding bearing arranged at two or more locations in the axial direction and at two or more locations perpendicular to the axial direction, and a lubricant provided on the side surface of the bearing 20. A dynamic pressure device containing a lubricant characterized in that a porous member 61 impregnated with a lubricant is attached to the reservoir portion 60 and the porous member 61 is brought into contact with the sliding surfaces 11 and 12 of the shaft body 10. Pertains to type plain bearings.
以下、この考案の実施例について、図面を参照
して説明する。 Examples of this invention will be described below with reference to the drawings.
第１図は、この考案をリニアーすべり軸受に適
用した実施例である。同図ａにおいて、符号１０
は軸体、１５はスリーブ、２０はスリーブ１５に
組込まれたリニアーすべり軸受を、それぞれ示
し、軸体１０のリニアー外面１１とリニアーすべ
り軸受２０のリニアー内面２１とがそれぞれ円筒
状のすべり面を形成し、軸体１０はリニアーすべ
り軸受２０に支承されて軸方向に往復直線運動す
る。このリニアーすべり軸受２０のリニアー内面
２１には、同図ｂ，ｃおよびｄに示すように、矢
じり状の動圧発生用のみぞ４０，５０が形成され
ている。同図ｂに示すみぞは、矢先方向が軸方向
右向き（同図ａのＡ方向）のみぞ４０と軸方向左
向き（同図ａのＢ方向）のみぞ５０とを軸方向に
ほぼ同一の間隔で交互に配設し、円周方向に適宜
の間隔をおいて配列してある。同図ｃに示すみぞ
は、矢先方向が軸方向右向きのみぞ４０と軸方向
左向きのみぞ５０とを菱形状に向い合わせて接続
し、この菱形状のみぞを軸方向にほぼ同一の間隔
となるようにして、円周方向に適宜の間隔をおい
て配列してある。同図ｄに示すみぞは、矢先方向
が軸方向右向きのみぞ４０と軸方向左向きのみぞ
５０とを波形状に接続して、この波形状のみぞを
軸方向にほぼ同一の間隔をおいて円周方向に配列
してある。 FIG. 1 shows an embodiment in which this invention is applied to a linear sliding bearing. In the same figure a, code 10
15 is a shaft body, 15 is a sleeve, and 20 is a linear sliding bearing incorporated in the sleeve 15, and the linear outer surface 11 of the shaft body 10 and the linear inner surface 21 of the linear sliding bearing 20 each form a cylindrical sliding surface. However, the shaft body 10 is supported by a linear sliding bearing 20 and makes linear reciprocating motion in the axial direction. The linear inner surface 21 of the linear sliding bearing 20 is formed with arrowhead-shaped grooves 40 and 50 for generating dynamic pressure, as shown in FIGS. The grooves shown in Figure b have grooves 40 whose arrowheads point to the axial right (direction A in figure a) and grooves 50 which point to the left in the axial direction (direction B in figure a) at approximately the same intervals in the axial direction. They are alternately arranged and arranged at appropriate intervals in the circumferential direction. The groove shown in figure c connects a groove 40 whose arrowheads point to the right in the axial direction and a groove 50 which points to the left in the axial direction facing each other in a diamond shape, and these diamond-shaped grooves are spaced at approximately the same intervals in the axial direction. In this way, they are arranged at appropriate intervals in the circumferential direction. The groove shown in FIG. They are arranged circumferentially.
これらの動圧発生用のみぞ４０，５０の深さ
は、数μm〜数10μmの範囲で適宜選定する。 The depth of these grooves 40, 50 for generating dynamic pressure is appropriately selected in the range of several μm to several tens of μm.
また、軸体１０のリニアー外面１１とリニアー
すべり軸受２０のリニアー内面２１との間の軸受
すき間１８は、数μm〜200μmの範囲とする。 Further, the bearing gap 18 between the linear outer surface 11 of the shaft body 10 and the linear inner surface 21 of the linear sliding bearing 20 is in the range of several μm to 200 μm.
上記のリニアーすべり軸受２０は、その軸方向
長さをスリーブ１５の軸方向長さよりも短かく成
形してスリーブ１５に組込まれており、スリーブ
１５とリニアーすべり軸受２０との両側端面との
間には、該軸受２０のリニアー内面２１側に開口
する環状の段部１６を形成して、該段部１６に
は、潤滑油を含浸させた多孔性部材６１を軸体１
０のリニアー外面１１に接触させて取り付けてい
る。多孔性部材６１は、吸油性にすぐれた素材を
フエルト状、あるいはスポンジ状にして成形した
ものを使用する。この多孔性部材６１は、含油さ
せる前に接着剤を用いてリニアーすべり軸受２０
の端面とスリーブ１５の内周面とに接着するか、
あるいはスリーブ１５の内周面に環状みぞを設け
て嵌め合わせ、リニアーすべり軸受２０の端面に
密着させる。 The above-mentioned linear slide bearing 20 is assembled into the sleeve 15 by molding its axial length to be shorter than the axial length of the sleeve 15, and is provided between both end surfaces of the sleeve 15 and the linear slide bearing 20. An annular step 16 is formed that opens on the linear inner surface 21 side of the bearing 20, and a porous member 61 impregnated with lubricating oil is inserted into the step 16.
It is attached in contact with the linear outer surface 11 of 0. The porous member 61 is made of a felt-like or sponge-like material with excellent oil absorption properties. This porous member 61 is attached to the linear sliding bearing 20 using adhesive before being impregnated with oil.
and the inner peripheral surface of the sleeve 15, or
Alternatively, an annular groove is provided on the inner circumferential surface of the sleeve 15 and the sleeve 15 is fitted into the sleeve 15 so as to be brought into close contact with the end surface of the linear slide bearing 20.
このようにして、リニアーすべり軸受２０の両
側端部に、含油多孔性部材６１による潤滑剤溜り
部６０が構成される。 In this way, lubricant reservoirs 60 are formed by the oil-impregnated porous members 61 at both end portions of the linear sliding bearing 20 .
上記構成のリニアーすべり軸受２０に支承され
た軸体１０が、軸方向に往復直線運動すると、多
孔性部材６１に含浸させてある潤滑油が、軸体１
０のリニアー外面１１に適度に付着して、リニア
ーすべり軸受２０との間の潤滑が行なわれる。軸
体１０の往復直線運動に伴つて軸体１０上の潤滑
油の付着量が減少しても、多孔性部材６１に含ま
れている潤滑油が、毛細管作用によつて軸体１０
側に滲出してくるから、常に適切な油量が保たれ
た状態で潤滑を行なうことができる。また、この
多孔性部材６１により軸受２０の両側端部と軸体
１０との間が密封された状態となるため、軸体１
０に塵埃その他の異物が付着した場合でも、軸受
２０内部への侵入を防止することができる。 When the shaft body 10 supported by the linear slide bearing 20 having the above-mentioned configuration makes a reciprocating linear movement in the axial direction, the lubricating oil impregnated in the porous member 61 is transferred to the shaft body 1.
It adheres appropriately to the linear outer surface 11 of 0, and lubrication between it and the linear sliding bearing 20 is performed. Even if the amount of lubricant oil deposited on the shaft body 10 decreases with the reciprocating linear movement of the shaft body 10, the lubricant oil contained in the porous member 61 is transferred to the shaft body 10 by capillary action.
Since it oozes out to the sides, lubrication can be performed with the appropriate amount of oil always maintained. In addition, since the porous member 61 creates a sealed state between both ends of the bearing 20 and the shaft body 10, the shaft body 10
Even if dust or other foreign matter adheres to the bearing 20, it can be prevented from entering the inside of the bearing 20.
上記構成の軸受において、軸体１０がＡ方向に
直線運動した場合は、この運動方向Ａに矢先方向
が一致する軸方向右向きのみぞ４０のポンピング
作用による動圧が発生して、矢先部分の圧力が高
くなり、リニアー外面１１とリニアー内面２１と
の間の軸受すき間１８には、矢先部分から流出し
た潤滑油による油膜が形成され、該油膜によつて
軸体１０が支持される。これと反対に、軸体１０
がＢ方向に直線運動した場合は、矢先方向がＢ方
向と一致する軸方向左向きのみぞ５０によるポン
ピング作用が発生して、このみぞ５０の矢先部分
から流出した潤滑油による油膜が、軸受すき間１
８に形成され、該油膜により軸体１０を支持す
る。 In the bearing configured as described above, when the shaft body 10 moves linearly in the direction A, dynamic pressure is generated due to the pumping action of the groove 40 facing right in the axial direction whose arrow head direction coincides with this movement direction A, and the pressure at the arrow head portion is generated. becomes higher, and an oil film is formed in the bearing gap 18 between the linear outer surface 11 and the linear inner surface 21 by the lubricating oil flowing out from the arrow tip portion, and the shaft body 10 is supported by the oil film. On the contrary, the shaft body 10
When the bearing moves linearly in the B direction, a pumping action is generated by the groove 50 facing leftward in the axial direction, the arrow tip of which coincides with the B direction, and an oil film of lubricating oil flowing out from the arrow tip of the groove 50 spreads across the bearing clearance 1.
8, and the shaft body 10 is supported by the oil film.
上記の軸受においては、動圧発生用のみぞ４
０，５０の配列を、同図ｂの場合では軸方向の両
端部と中間部とに、同図ｃ及びｄの場合も同様に
軸方向の両端部と中間部とに、それぞれ３列にし
てあるから、軸体１０がＡおよびＢの正逆何れの
方向に直線運動しても、軸方向の少なくとも３箇
所において等しい動圧が発生することになる。 In the above bearing, the groove 4 for generating dynamic pressure is
0 and 50 are arranged in three rows at both ends and the middle part in the axial direction in the case of b in the same figure, and in the same way in both ends and the middle part in the axial direction in the case of c and d in the same figure. Therefore, even if the shaft body 10 moves linearly in either the forward or reverse directions of A and B, equal dynamic pressure will be generated at at least three locations in the axial direction.
上記実施例では、リニアーすべり軸受２０を固
定して軸体１０が往復直線運動する場合について
説明したが、軸体１０を固定してリニアーすべり
軸受２０が往復直線運動する場合についても同様
に適用することができる。 In the above embodiment, a case has been described in which the linear slide bearing 20 is fixed and the shaft body 10 moves linearly back and forth, but the same applies to the case where the shaft body 10 is fixed and the linear slide bearing 20 moves linearly back and forth. be able to.
また、動圧発生用のみぞ４０，５０は、リニア
ーすべり軸受２０のリニアー内面２１でなく、軸
体１０のリニアー外面１１に設けてもよく、さら
に、リニアー内面２１とリニアー外面１１との双
方に設けることもできる。 Further, the grooves 40 and 50 for generating dynamic pressure may be provided not on the linear inner surface 21 of the linear plain bearing 20 but on the linear outer surface 11 of the shaft body 10, and furthermore, the grooves 40 and 50 for generating dynamic pressure may be provided on both the linear inner surface 21 and the linear outer surface 11. It is also possible to provide one.
第２図は、潤滑剤溜り部６０の他の実施例を示
したものである。 FIG. 2 shows another embodiment of the lubricant reservoir 60.
第２図の実施例においては、一対のリニアーす
べり軸受２０ａ，２０ｂを、スリーブ１５の中央
部で適宜の間隔をおいて対向させ、該軸受２０
ａ，２０ｂの対向端面とスリーブ１５の内周面と
によつて形成された環状の凹部１７に、潤滑油を
含浸させた多孔性部材６１を嵌入して軸体１０の
リニアー外面１１に接触させている。また、スリ
ーブ１５の中央部には、給油孔１９が設けてあ
る。 In the embodiment shown in FIG.
A porous member 61 impregnated with lubricating oil is fitted into the annular recess 17 formed by the opposing end surfaces of the sleeves 15a and 20b and the inner circumferential surface of the sleeve 15, and brought into contact with the linear outer surface 11 of the shaft body 10. ing. Further, an oil supply hole 19 is provided in the center of the sleeve 15 .
この実施例によると、多孔性部材６１が軸受２
０の内部に密閉された状態となるから、多量の潤
滑油を含浸させて内蔵させることができ、潤滑油
の蒸発による消耗を防止することが可能となる。
また、必要に応じて給油孔１９から潤滑油を補給
することもできる。 According to this embodiment, the porous member 61 is
Since it is in a sealed state inside the 0, a large amount of lubricating oil can be impregnated and built in, making it possible to prevent consumption due to evaporation of the lubricating oil.
Furthermore, lubricating oil can be supplied from the oil supply hole 19 as needed.
この多孔性部材６１には、潤滑油のほか、低粘
度のグリースを含浸させてもよい。 This porous member 61 may be impregnated with low-viscosity grease in addition to lubricating oil.
第３図および第４図は、それぞれリニアーすべ
り軸受の他の実施例であり、軸体と軸受とが平面
状のすべり面を介して軸方向に相対的に往復直線
運動する場合について、この考案を適用したもの
である。 Figures 3 and 4 show other embodiments of the linear sliding bearing, respectively, and the invention is based on the case where the shaft body and the bearing move relatively linearly back and forth in the axial direction via a flat sliding surface. is applied.
第３図は、軸体１０の軸方向に突出して設けた
三角形状の摺動部１０ａの両側傾斜面をリニアー
外面１１とし、このリニアー外面１１とこれに接
触する軸受２０のリニアー内面２１とのすべり面
の何れか一方、もしくは双方に、第１図に示した
動圧発生用のみぞを矢先方向が往復直線運動方向
に一致するように配列して設けている。軸受２０
が組込まれた軸受保持体１５ａの両側端面には、
潤滑剤を含浸させた多孔性部材６１を接着して軸
体１０のリニアー外面１１に接触させてあり、こ
の含油多孔性部材６１が潤滑剤溜り部６０を構成
している。 In FIG. 3, the inclined surfaces on both sides of the triangular sliding portion 10a protruding in the axial direction of the shaft body 10 are defined as linear outer surfaces 11, and the linear outer surface 11 and the linear inner surface 21 of the bearing 20 in contact with the linear outer surface 11 are shown in FIG. Grooves for generating dynamic pressure as shown in FIG. 1 are arranged on one or both of the sliding surfaces so that the direction of the arrowheads coincides with the direction of reciprocating linear movement. Bearing 20
On both end surfaces of the bearing holder 15a in which the bearing holder 15a is incorporated,
A porous member 61 impregnated with a lubricant is bonded and brought into contact with the linear outer surface 11 of the shaft body 10, and this oil-impregnated porous member 61 constitutes a lubricant reservoir 60.
第４図は、軸体１０の軸方向に突出して設けた
直方形状の摺動部１０ａの両側垂直面とこの垂直
面の下端縁に交接する水平面とにリニアー外面１
１が形成され、このリニアー外面１１とこれに接
触する軸受２０のリニアー内面２１とのすべり面
の何れか一方、もしくは双方に第１図に示した動
圧発生用のみぞを矢先方向が往復直線運動方向に
一致するように配列している。上記軸受２０が組
込まれた軸受保持体１５ａの内面の中央部に、適
宜の軸方向幅の凹部１７を軸方向に対して直角方
向に形成し、この凹部１７に、潤滑油を含浸させ
た多孔性部材６１を嵌入して軸体１０のリニアー
外面１１に接触させてある。この凹部１７には、
含油多孔性部材６１に代えてグリースのみを充填
することもできる。 FIG. 4 shows a linear outer surface 1 on both vertical surfaces of a rectangular sliding portion 10a provided protruding in the axial direction of the shaft body 10 and a horizontal surface that intersects with the lower end edge of this vertical surface.
1 is formed, and one or both of the sliding surfaces between this linear outer surface 11 and the linear inner surface 21 of the bearing 20 that is in contact with the linear outer surface 11 have grooves for generating dynamic pressure as shown in FIG. They are arranged to match the direction of movement. A recess 17 having an appropriate axial width is formed in a direction perpendicular to the axial direction in the center of the inner surface of the bearing holder 15a in which the bearing 20 is incorporated, and this recess 17 has porous holes impregnated with lubricating oil. The elastic member 61 is fitted and brought into contact with the linear outer surface 11 of the shaft body 10. In this recess 17,
It is also possible to fill only grease instead of the oil-impregnated porous member 61.
第５図は、この考案をラジアル・リニアーすべ
り軸受に適用した実施例である。同図ａにおい
て、軸体１０のラジアル・リニアー外面１２とラ
ジアル・リニアーすべり軸受３０のラジアル・リ
ニアー内面３１とが円筒状のすべり面を形成し、
軸体１０もしくは軸受３０が、らせん状に往復運
動する。同図ｂ，ｃ，ｄは、それぞれラジアル・
リニアーすべり軸受３０のラジアル・リニアー内
面３１に形成した矢じり状の動圧発生用のみぞ４
０，５０の形状と配列とを示す。同図ｂでは、矢
先方向が軸体１０のリード角θ方向に位置する下
向きのみぞ４０と上向きのみぞ５０とを交互にリ
ード角θ方向と平行に配列してある。同図ｃで
は、矢先方向がリード角θ方向に位置する下向き
のみぞ４０と上向きのみぞ５０とを菱変状に接続
して、円周方向に４列となるようにしてリード角
θ方向と平行に配列してある。同図ｄでは、矢先
方向がリード角θ方向に位置する下向きのみぞ４
０と上向きのみぞ５０とを波形状に接続して、こ
の下向きのみぞ４０と上向きのみぞ５０とがリー
ド角θ方向と平行となるように配列してある。 FIG. 5 shows an embodiment in which this invention is applied to a radial linear sliding bearing. In Figure a, the radial linear outer surface 12 of the shaft body 10 and the radial linear inner surface 31 of the radial linear sliding bearing 30 form a cylindrical sliding surface,
The shaft body 10 or the bearing 30 reciprocates in a spiral manner. b, c, and d in the same figure are radial and
Arrowhead-shaped groove 4 for generating dynamic pressure formed on the radial linear inner surface 31 of the linear sliding bearing 30
0,50 shape and arrangement are shown. In FIG. 1B, downward grooves 40 and upward grooves 50 whose arrowheads are located in the lead angle θ direction of the shaft body 10 are alternately arranged parallel to the lead angle θ direction. In Figure c, downward grooves 40 and upward grooves 50, whose arrowheads are located in the lead angle θ direction, are connected in a rhombic shape so that they form four rows in the circumferential direction. They are arranged in parallel. In figure d, the downward groove 4 whose arrowhead direction is located in the lead angle θ direction
0 and the upward groove 50 are connected in a wave shape, and the downward groove 40 and the upward groove 50 are arranged in parallel to the lead angle θ direction.
上記の動圧発生用のみぞ４０，５０は、軸体１
０のラジアル・リニアー外面１２に設けてもよ
く、また、ラジアル・リニアー内面３１とラジア
ル・リニアー外面１２との双方に設けることもで
きる。 The grooves 40 and 50 for generating dynamic pressure are formed in the shaft body 1.
0 may be provided on the radial linear outer surface 12, or may be provided on both the radial linear inner surface 31 and the radial linear outer surface 12.
また、上記ラジアル・リニアーすべり軸受３０
の両側端面には、第１図の実施例と同様に、含油
多孔性部材６１からなる潤滑剤溜り部６０が設け
てある。 In addition, the above radial/linear sliding bearing 30
A lubricant reservoir 60 made of an oil-impregnated porous member 61 is provided on both end surfaces of the lubricant reservoir 60, as in the embodiment shown in FIG.
上記構成の軸体１０、もしくはラジアル・リニ
アーすべり軸受３０が、往復回転直線運動すると
きの潤滑は、第１図の場合と同様に多孔性部材６
１から滲出する潤滑油によつて行なわれる。 When the shaft body 10 or the radial/linear sliding bearing 30 having the above configuration makes reciprocating rotational linear motion, lubrication is provided by the porous member 6 as in the case of FIG.
This is done by lubricating oil exuding from 1.
また、軸体１０がＣ方向に回転直線運動すると
きは、Ｃ方向に矢先方向が一致するリード角θ方
向下向きのみぞ４０のポンピング作用による動圧
が発生し、これと反対のＤ方向に回転直線運動す
るときは、Ｄ方向に矢先方向が一致するリード角
θ方向上向きのみぞ５０のポンピング作用による
動圧が発生して、それぞれ、みぞ４０，５０の矢
先部分から潤滑油が軸受すき間１８に流出して形
成される油膜によつて軸体１０が支承される。軸
受２０がＣ方向またはＤ方向に回転直線運動する
ときは、それぞれみぞ５０またはみぞ４０によつ
て同様に軸受２０が支承される。 Furthermore, when the shaft body 10 rotates and moves linearly in the C direction, dynamic pressure is generated due to the pumping action of the downward groove 40 in the lead angle θ direction whose arrowhead direction coincides with the C direction, and it rotates in the D direction opposite to this. During linear motion, dynamic pressure is generated by the pumping action of the grooves 50 facing upward in the lead angle θ direction whose arrowheads coincide with the D direction, and lubricating oil flows into the bearing gap 18 from the arrowheads of the grooves 40 and 50, respectively. The shaft body 10 is supported by the oil film formed by the outflow. When the bearing 20 makes rotational linear motion in the C direction or the D direction, the bearing 20 is similarly supported by the groove 50 or the groove 40, respectively.
上記の軸受においても、動圧発生用のみぞ４
０，５０は、同図ｂおよびｄの場合では、リード
角θ方向の両端部と中間部とに配列され、同図ｃ
の場合では、リード角θ方向の両端部とその中間
に４列に配列されているから、軸体１０もしくは
ラジアル・リニアーすべり軸受３０がＣおよびＤ
の正逆何れの方向に回転直線運動しても、軸方向
の少なくとも３個所において等しい動圧が発生す
る。 Also in the above bearing, the groove 4 for generating dynamic pressure
0 and 50 are arranged at both ends and the middle part in the lead angle θ direction in cases b and d of the same figure, and in the case of c of the same figure,
In the case of , the shaft body 10 or the radial linear plain bearing 30 is arranged in four rows at both ends and in the middle in the direction of the lead angle θ.
Even if the rotary linear motion is performed in either the forward or reverse direction, equal dynamic pressure is generated at at least three locations in the axial direction.
多孔性部材６１の取付位置は、第２図のように
軸受３０の中央部としてもよく、また多孔性部材
６１に代えて第３図のようにグリースを充填して
もよい。 The porous member 61 may be mounted at the center of the bearing 30 as shown in FIG. 2, or may be filled with grease instead of the porous member 61 as shown in FIG.
前記各実施例における動圧発生用のみぞ４０，
５０の深さは、前述したように数μm〜数10μmで
あるから、このみぞ４０，５０以外のすべり面だ
けでなく、みぞ４０，５０の部分でも負荷を受け
ることができるため、接触面圧が小さく、耐摩耗
性が著しく向上するが、軸受２０，３０の材質を
合成樹脂とすることにより、さらに耐摩耗性を増
大させることができる。 Groove 40 for generating dynamic pressure in each of the above embodiments,
As mentioned above, the depth of groove 50 is from several μm to several tens of μm, so not only the sliding surface other than grooves 40 and 50 but also the grooves 40 and 50 can receive load, so the contact surface pressure However, by using synthetic resin as the material for the bearings 20 and 30, the wear resistance can be further increased.
また、動圧発生用のみぞ４０，５０の配列数
は、必ずしも同数とする必要はなく、軸体と軸受
との運動方向に対応する負荷の大きさが異なる場
合は、たとえば矢先方向が正方向の運動方向と一
致するみぞの配列数を、矢先方向が逆方向の運動
方向と一致するみぞの配列数よりも多くして、そ
れぞれの運転条件に適切な配列数とすることがで
きる。 In addition, the number of grooves 40 and 50 for generating dynamic pressure does not necessarily have to be the same, and if the magnitude of the load corresponding to the direction of movement of the shaft body and bearing is different, for example, the direction of the arrow is in the positive direction. The number of grooves arranged in the same direction as the direction of movement can be made larger than the number of grooves arranged in the direction of movement in the opposite direction, so that the number of grooves in the arrangement is appropriate for each operating condition.
また、前記各実施例では、スリーブと軸受とが
別体となつているが、スリーブと軸受とを同一材
質で一体成形することもできる。 Further, in each of the above embodiments, the sleeve and the bearing are separate bodies, but the sleeve and the bearing can also be integrally molded from the same material.
以上、説明したところから明らかなように、こ
の考案は、軸体と軸受とのすべり面の少なくとも
一方に、矢先方向が軸体と軸受の直線運動、もし
くは回転直線運動の一方向と一致する矢じり状の
みぞと、これと反対の運動方向に矢先方向が一致
する矢じり状のみぞとを、それぞれすべり面の運
動方向と平行に配列して設け、軸受の側面に設け
た潤滑剤溜り部に、潤滑剤を含浸させた多孔性部
材を取り付けて軸体のすべり面に接触させる構成
としている。したがつて、この考案によれば、軸
体もしくは軸受が正逆何れの方向に運動した場合
でも軸体と軸受とのすべり面で動圧を発生させる
ことが可能となる。 As is clear from the above explanation, this invention uses an arrowhead whose arrow head direction coincides with one direction of the linear motion or rotational linear motion of the shaft and the bearing on at least one of the sliding surfaces of the shaft and the bearing. A lubricant reservoir provided on the side surface of the bearing is provided with grooves in the shape of a shape and grooves in the shape of an arrow whose arrowhead direction coincides with the direction of movement opposite to the grooves, respectively, arranged parallel to the direction of movement of the sliding surface. A porous member impregnated with lubricant is attached and brought into contact with the sliding surface of the shaft. Therefore, according to this invention, it is possible to generate dynamic pressure on the sliding surface between the shaft and the bearing even when the shaft or the bearing moves in either the forward or reverse direction.
また、矢先方向が一方の運動方向に一致するみ
ぞと他方の運動方向に一致するみぞとは、いずれ
も軸方向の二ヶ所以上で、かつ軸方向と直交する
方向の二ヶ所以上に配列してあるので、軸体と軸
受とのいずれか一方は他方に対して軸方向の二ヶ
所以上および軸方向と直交する方向の二ヶ所以上
で支持され、安定した運動をすることができる。 Additionally, grooves whose arrowheads coincide with one direction of motion and grooves whose arrowheads coincide with the other direction of motion are arranged at two or more locations in the axial direction and at two or more locations in the direction perpendicular to the axial direction. Therefore, either one of the shaft body and the bearing is supported relative to the other at two or more locations in the axial direction and at two or more locations in a direction perpendicular to the axial direction, thereby allowing stable movement.
また、この考案によれば、軸受に内蔵された潤
滑油もしくはグリース等の潤滑剤が多孔性部材を
介して軸体のすべり面に接触した状態で軸体もし
くは軸受が運動するから、常時、うすく、適量の
潤滑剤が軸体と軸受とのすべり面に移転し、軸受
すき間に必要最小限度の油膜もしくはグリース膜
を形成することができる。このため、軸体と軸受
とのストローク長の両側端部から漏出する潤滑油
もしくはグリースの量を最小限度に抑制すること
ができ、潤滑油切れやグリース切れを起こすこと
がないから、長期間に亘つて潤滑剤を補給せずに
使用することが可能となる。 In addition, according to this invention, the shaft or bearing moves while the lubricant such as lubricant oil or grease contained in the bearing is in contact with the sliding surface of the shaft through the porous member, so that the lubricant such as lubricant oil or grease contained in the bearing is always in contact with the sliding surface of the shaft. , an appropriate amount of lubricant is transferred to the sliding surface between the shaft body and the bearing, and the minimum necessary oil film or grease film can be formed in the bearing gap. Therefore, the amount of lubricating oil or grease leaking from both ends of the stroke length of the shaft body and bearing can be suppressed to a minimum, and as there is no possibility of running out of lubricating oil or grease, it will last for a long time. It becomes possible to use the product without replenishing lubricant.
さらに、この考案によれば、潤滑油やグリース
の漏出がきわめて少なくなることにより、軸受周
辺の機材の汚染を防止できる効果が併せて得られ
る。 Furthermore, according to this invention, the leakage of lubricating oil and grease is extremely reduced, which also provides the effect of preventing contamination of equipment around the bearing.
第１図は、リニアーすべり軸受についてのこの
考案の実施例を示し、同図ａはその縦断面図、同
図ｂないしｄはそれぞれリニアー内面の動圧発生
用のみぞを示す展開図、第２図は、潤滑剤溜り部
の他の実施例を示す縦断面図、第３図および第４
図は、それぞれリニアーすべり軸受についての他
の実施例を示し、第３図ａは正面図、第３図ｂは
第３図ａのＺ−Ｚ線断面図、第３図ｃは側面図、
第４図ａは正面図、第４図ｂおよびｃは、それぞ
れ第４図ａのＸ−Ｘ線断面図およびＹ−Ｙ線断面
図、第５図はラジアル・リニアーすべり軸受につ
いてのこの考案の実施例を示し、同図ａはその縦
断面図、同図ｂないしｄはそれぞれラジアル・リ
ニアー内面の動圧発生用のみぞを示す展開図であ
る。
図中、１０は軸体、１１，１２はそれぞれ軸体
のリニアー外面、ラジアル・リニアー外面（すべ
り面）、２０はリニアーすべり軸受、２１はその
リニアー内面（すべり面）、３０はラジアル・リ
ニアーすべり軸受、３１はそのラジアル・リニア
ー内面（すべり面）、４０，５０は動圧発生用の
みぞ、６０は潤滑剤溜り部、６１は多孔性部材で
ある。
Fig. 1 shows an embodiment of this invention for a linear sliding bearing, in which Fig. 1a is a longitudinal sectional view, Fig. 1b to d are exploded views showing grooves for generating dynamic pressure on the linear inner surface, and Fig. 2 3 and 4 are longitudinal sectional views showing other embodiments of the lubricant reservoir.
The figures show other embodiments of the linear sliding bearing, respectively: FIG. 3a is a front view, FIG. 3b is a sectional view taken along the Z-Z line of FIG. 3a, and FIG. 3c is a side view.
4a is a front view, FIGS. 4b and 4c are sectional views taken along the lines X-X and Y-Y of FIG. 4a, respectively, and FIG. An embodiment is shown in which Figure a is a longitudinal sectional view thereof, and Figures b to d are exploded views showing grooves for generating dynamic pressure on the radial and linear inner surfaces, respectively. In the figure, 10 is the shaft body, 11 and 12 are the linear outer surface and radial linear outer surface (sliding surface) of the shaft body, 20 is the linear sliding bearing, 21 is its linear inner surface (sliding surface), and 30 is the radial linear sliding surface. In the bearing, 31 is its radial linear inner surface (sliding surface), 40 and 50 are grooves for generating dynamic pressure, 60 is a lubricant reservoir, and 61 is a porous member.
Claims (1)
向の直線運動が相対的に可能であり、前記すべり
面の少なくとも一方に、矢じり状の動圧発生用の
みぞが形成され、該動圧発生用のみぞは、矢先方
向が軸体と軸受との一方向の運動方向に一致する
みぞと、矢先方向が他方の運動方向に一致するみ
ぞとを、それぞれ前記すべり面に備え、矢先方向
が一方の運動方向に一致するみぞと他方の運動方
向に一致するみぞとは、いずれも軸方向の二ヶ所
以上に配列されると共に軸方向と直交する方向の
二ヶ所以上に配列された動圧形すべり軸受であつ
て、前記軸受の側面に設けた潤滑剤溜り部に、潤
滑剤を含浸させた多孔性部材を取り付け、該多孔
性部材を軸体のすべり面に接触させたことを特徴
とする潤滑剤を内蔵する動圧形すべり軸受。 The shaft body and the bearing are relatively capable of linear movement in forward and reverse directions via mutual sliding surfaces, and an arrowhead-shaped groove for generating dynamic pressure is formed on at least one of the sliding surfaces, and the movement The pressure generating groove is provided with a groove in which the direction of the arrow corresponds to one direction of movement of the shaft body and the bearing, and a groove whose direction of the arrow corresponds to the direction of movement in the other direction, respectively, on the sliding surface. Grooves that coincide with one direction of motion and grooves that coincide with the other direction of motion are both arranged at two or more locations in the axial direction and at two or more locations in a direction perpendicular to the axial direction. A sliding bearing, characterized in that a porous member impregnated with lubricant is attached to a lubricant reservoir provided on a side surface of the bearing, and the porous member is brought into contact with the sliding surface of the shaft body. A hydrodynamic sliding bearing with a built-in lubricant.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3644883U JPS59142514U (en) | 1983-03-14 | 1983-03-14 | Dynamic pressure plain bearing with built-in lubricant |
| FR8313668A FR2532382B1 (en) | 1982-08-25 | 1983-08-24 | GUIDE TO LUBRICATING GROOVES FOR RECLINE LINEAR MOVEMENT |
| US06/526,560 US4491373A (en) | 1982-08-25 | 1983-08-25 | Construction of the mating sliding members in a linear feeding means |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3644883U JPS59142514U (en) | 1983-03-14 | 1983-03-14 | Dynamic pressure plain bearing with built-in lubricant |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS59142514U JPS59142514U (en) | 1984-09-22 |
| JPH0311459Y2 true JPH0311459Y2 (en) | 1991-03-19 |
Family
ID=30167123
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3644883U Granted JPS59142514U (en) | 1982-08-25 | 1983-03-14 | Dynamic pressure plain bearing with built-in lubricant |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59142514U (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0618058B2 (en) * | 1984-08-18 | 1994-03-09 | 松下電器産業株式会社 | Fluid bearing cylinder device |
| JP4702186B2 (en) * | 2006-05-31 | 2011-06-15 | 日産自動車株式会社 | Low friction sliding member |
| JP4512831B2 (en) * | 2006-10-11 | 2010-07-28 | 国立大学法人鳥取大学 | Sliding linear motion guide device |
| JP5104180B2 (en) * | 2007-10-09 | 2012-12-19 | 株式会社ジェイテクト | Feed guide device |
| JP5496575B2 (en) * | 2009-08-25 | 2014-05-21 | キヤノンマシナリー株式会社 | Sliding surface |
| US8567227B2 (en) * | 2010-02-05 | 2013-10-29 | Dadco, Inc. | Guide and retention assembly for a die set |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5332252A (en) * | 1976-09-03 | 1978-03-27 | Philips Nv | Bearing |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5466043U (en) * | 1977-10-20 | 1979-05-10 | ||
| JPS55148356U (en) * | 1979-04-09 | 1980-10-25 |
-
1983
- 1983-03-14 JP JP3644883U patent/JPS59142514U/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5332252A (en) * | 1976-09-03 | 1978-03-27 | Philips Nv | Bearing |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS59142514U (en) | 1984-09-22 |
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