JPS58137619A - Static-pressure thrust bearing - Google Patents
Static-pressure thrust bearingInfo
- Publication number
- JPS58137619A JPS58137619A JP1984582A JP1984582A JPS58137619A JP S58137619 A JPS58137619 A JP S58137619A JP 1984582 A JP1984582 A JP 1984582A JP 1984582 A JP1984582 A JP 1984582A JP S58137619 A JPS58137619 A JP S58137619A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- annular
- thrust bearing
- hydrostatic
- outer 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.)
- Pending
Links
Landscapes
- Magnetic Bearings And Hydrostatic Bearings (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
本ｍ＊は可蜜若しく嬬−冑Ｏｗ！ストンスト買−り會持
つ軸式静水静力学的−電機若しくは原―機Ｏピストｙｏ
ｗｉｖｈプ＊、、ｔｌにｑＩに適会してか１゜高圧力高
回転下で作動する静圧スラスト軸受に関する。[Detailed Description of the Invention] This m* is Kamitsu or Tsumu Ow! Axial type hydrostatic-electric or original machine O-piste with a stone strike purchase meeting
The present invention relates to a hydrostatic thrust bearing that operates under high pressure and high rotation by 1° by matching wivhp*, tl and qI.
軸式静水力学的発電機若しくは原動機のピストンの摺動
プ四ツクに応用される静圧スラスト軸受の従来公知の最
も単純なものは円形の外形を持ちその中心部に円形の凹
所管備え、その凹所に入口チャンネルが開口する構造の
ものである。動力損失についていえば円形凹所の直径の
、軸受の外径に対する最適な比は大体０．６である。−
この従来の欠点は、高入圧力若しくは高回転の隙巾にピ
ストンの荷重に対する軸受力が減少するととＫあり。The simplest known hydrostatic thrust bearing, which is applied to the sliding shaft of the piston of an axial hydrostatic generator or prime mover, has a circular outer shape with a circular concave pipe in its center. It has a structure in which an inlet channel opens in a recess. In terms of power losses, the optimum ratio of the diameter of the circular recess to the outer diameter of the bearing is approximately 0.6. −
The disadvantage of this conventional method is that the bearing force against the piston load decreases due to high input pressure or high rotation speed.
これは加えられる作動流体％に鉱物油の圧力及び一度に
対する粘性に依存して引起されるものである。他の従来
例では作動流体の粘性に対する軸受力の依存を減少する
丸めバッキング面の外１１に環状凹所を設け、バッキン
グ面と環状摺動面との分離を行うているものがある。環
状凹所はドレンチャンネルを介してクエスト空間と連結
している故に流体動力学的ベアリングとして横筒・する
、バッキ３／／Ｉｆの外径ＯＲ状ａｕｉの掻に対する比
率は普通０．８から０．８５であＬこれＫより作−流体
の粘度変化に対する軸受０軸受カの依存性唸かなりに減
少する。しかし同時に軸受内の通過損失は増大する。外
肯の環状ｗＦｉ不平衡な軸方向力をとらえ同時にこれは
案内ｉ１に対する軸受の角変安定性を増大させる。軸受
の外径は拡大してお〕シリンダブ讐ツクの空間内のピス
トン最大径に至ることは不可能であり、その丸め出方パ
ラメータ及びコンバータのウェイトワンのみならず効率
がかなり減少する。This is caused by the pressure and viscosity of the mineral oil relative to the applied working fluid percentage. Another prior art example includes an annular recess on the outside 11 of the rounded backing surface to reduce the dependence of the bearing force on the viscosity of the working fluid, thereby separating the backing surface and the annular sliding surface. Since the annular recess is connected to the quest space through the drain channel, it is used as a horizontal cylinder as a hydrodynamic bearing.The ratio of the outer diameter of the back 3//If to the outer diameter of the OR shape aui is usually 0.8 to 0. At .85, the dependence of the bearing force on the viscosity change of the working fluid is significantly reduced. However, at the same time, the passing losses within the bearing increase. The circumferential annular wFi captures the unbalanced axial forces and at the same time this increases the angular stability of the bearing relative to guide i1. Although the outer diameter of the bearing is enlarged, it is not possible to reach the maximum diameter of the piston in the space of the cylinder valve, and its rounding parameters and the efficiency as well as the weight of the converter are considerably reduced.
以上述べ九欠点は本発明の静圧スラスト軸受によって克
服される。即に本発明によれば、中心部の円形凹所、＃
円形凹所に開口する送出チャンネル、バッキング面及び
環状凹所を有する円形の外形を持つ静圧スラスト軸受に
おいて、バッキング面は環状凹所の両１１１に配置して
いる。バッキング面の外径と環状凹所の長径との差は環
状凹所の短径とバッキング面の内径との差より大きい、
環状凹所の第１の深さの１円形凹所の第１の深さに対す
る比は０．２からＯ６馨に設定される。The nine drawbacks mentioned above are overcome by the hydrostatic thrust bearing of the present invention. Immediately according to the invention, a central circular recess, #
In a hydrostatic thrust bearing with a circular profile having a delivery channel opening into a circular recess, a backing surface and an annular recess, the backing surface is located on both sides 111 of the annular recess. The difference between the outer diameter of the backing surface and the major axis of the annular recess is greater than the difference between the minor diameter of the annular recess and the inner diameter of the backing surface.
The ratio of the first depth of the annular recess to the first depth of the circular recess is set from 0.2 to O6.
本発明に係る静圧スラスト軸受の利点は摩擦および通過
損失が小さく１作動流体の粘性娶化に対する軸受力の依
存性が減少し、案内面に対する角度安定性が増大するこ
とにある。これに加えて生産が容品となり軸受の外径が
ピストンの径に対するシリンダブロック内の空間の最大
利用を可能するように設定でき、コンバータの出力及び
効率を増す。The advantages of the hydrostatic thrust bearing according to the invention are that friction and passage losses are low, the dependence of the bearing force on the viscosity of the working fluid is reduced, and the angular stability with respect to the guide surface is increased. In addition to this, production becomes more convenient and the outer diameter of the bearing can be set to allow maximum utilization of the space within the cylinder block relative to the diameter of the piston, increasing the power and efficiency of the converter.
以下本発明の好ましい実施形態を図面によって説明する
。Preferred embodiments of the present invention will be described below with reference to the drawings.
摺動ブロック１内に送出チャンネル２が形成され、その
チャンネル２を介し作動流体が円形凹所３に入り、その
円形凹所３から作動流体は静圧スラスト軸受のバッキン
グ面４と案内面５との間の隙間を通る。環状凹所６が次
のように作られる。A delivery channel 2 is formed in the sliding block 1, through which the working fluid enters a circular recess 3, from which the working fluid flows between the backing surface 4 and the guide surface 5 of the hydrostatic thrust bearing. pass through the gap between The annular recess 6 is made as follows.
即ち、バッキング面４がその環状凹所６の両側にされ、
環状凹所６は摺動ブロック１と摺動面５との間の摩擦損
失ｅｆｔ％際上関部上関与よ５に＆りているのである。That is, the backing surface 4 is on both sides of the annular recess 6,
The annular recess 6 contributes to the friction loss ef% between the sliding block 1 and the sliding surface 5.
もし摺動ブロックｌの静圧スラスト軸受及びその案内面
器の平行度が変化すれば相補的な静水力学的力が円形凹
所６の長手ｓｒ、とバッキング面４の外内＄ｒ４との間
の部分に生じ。If the parallelism of the hydrostatic thrust bearing of the sliding block l and its guide surface changes, a complementary hydrostatic force will be generated between the longitudinal length sr of the circular recess 6 and the outer and inner $r4 of the backing surface 4. Occurs in the area.
この付加的な静水力学的力が平行度の前記変化に対して
作用する０％し、摺動ブロック１のバッキング面が案内
面ＳＫ急速接近すればこれらの表面間の液体は押し出さ
れ、これ轄静圧ｐｄを生じさせ、この圧力は環状凹所６
内にも働自、静水力学的なダンピング力を増大させ、か
くして案内Ｈ５に対するバッキング面４の接近速度を減
少させる。If this additional hydrostatic force acts on the said change in parallelism and the backing surface of the sliding block 1 rapidly approaches the guide surface SK, the liquid between these surfaces will be forced out and A static pressure pd is created, which pressure is applied to the annular recess 6
This also increases the hydrostatic damping force and thus reduces the speed of approach of the backing surface 4 to the guide H5.
それ故に、静圧軸受の動的剛直性は増大する。環状凹所
６の第２の深さｈｌは圧力ｐ３の急速伝達の故に最少の
ものとすべ自ものであり１円形凹所３の第１の深さｈｌ
は円形凹所３の全空間にわたっての圧力ｐ、を均一に伝
達させるための４のである。Therefore, the dynamic stiffness of the hydrostatic bearing is increased. The second depth hl of the annular recess 6 is the smallest and smoothest due to the rapid transmission of the pressure p3, and the first depth hl of the circular recess 3
4 in order to uniformly transmit the pressure p over the entire space of the circular recess 3.
半４１ ｒｌ参ｒｓｅ ｒｌ、 ｒ４１０椙互の比を有
利に選定すゐことで支持力、力損失及び動的剛直性に対
する軸受の所望の特性を得ることができる。静水力学的
な力を斃生させる軸受の全表面を利用することでシリン
ダブロック内の空間の最大限利用可能とすや寸法のピス
トンを軸受に設けることが実現する。By advantageously selecting the ratio between half-41 rl, rse rl, and r410, the desired characteristics of the bearing with respect to bearing capacity, force loss and dynamic stiffness can be obtained. By utilizing the entire surface of the bearing that generates hydrostatic forces, it is possible to maximize the use of the space within the cylinder block and to provide the bearing with a snugly sized piston.
環状凹所によって作られるバッキング面４０２つの部分
は軸受の通過損失を減少させる。The two parts of the backing surface 40 created by the annular recess reduce bearing passage losses.
本発明を以上実施例によって説明したが本発明はこれに
限定されす、゛本発明の範囲内で種々の変形が可能であ
る。５Although the present invention has been described above using examples, the present invention is not limited to these examples; however, various modifications can be made within the scope of the present invention. 5
第１図は摺動ブロックの流体静力学スラスト軸受の一面
を示す図。
第２図は、第１図の＾−ム線に沿う断面図。
第３図は軸受内の流体静力学圧力の線図。
第４図は摺動ブロックとその案内面との間の間隙が急激
減少したときの流体静力学圧力の線図。
１・・・シリンダブ四ツク
２・・・送出チャンネル
３・・・円形凹所
４・・・バッキング面
５・・・案内面
６・・・環状、凹所
ｐｌ・・・円形凹所内圧力
ＰＩ・・・環状凹所内圧力
ｐｄ・・・動 圧
り、・・・第ｉ＠さ ・
ｈ重・・・第２１１さ
ｒ凰・・・内 径
ｒ、・・・小 径
ｒ、・・・長径
ｒ４・・・外径
特許出願人
雫１ぐｆイ タズケホ スト田ジャルストパ。
ナロトムイ ポドニク
特許出願代理人
弁理士 實 木 朗
弁瑠士西舘和之
弁理士 中 山 恭 介
弁理士 山 口 昭 之FIG. 1 is a view showing one side of the hydrostatic thrust bearing of the sliding block. FIG. 2 is a sectional view taken along the ^-mu line in FIG. 1. FIG. 3 is a diagram of hydrostatic pressure within the bearing. FIG. 4 is a diagram of hydrostatic pressure when the gap between the sliding block and its guide surface decreases rapidly. 1... Four cylinder tabs 2... Delivery channel 3... Circular recess 4... Backing surface 5... Guide surface 6... Annular, recess pl... Circular recess internal pressure PI.・Pressure inside the annular recess pd...dynamic pressure,...i@th, h weight...211th r 凰...inner diameter r,...small diameter r,...long diameter r4... Outer diameter patent applicant Shizuku 1guf I Tazukehosuto Tajarustopa. Narotomy Podnik Patent Attorney Patent Attorney Ben Rushi Minori Kazuyuki Nishidate Patent Attorney Kyo Nakayama Patent Attorney Akira Yamaguchi
Claims (1)
ンネルｓ Ａ ｙ ｄＰ／ダ面及びｌｌｌ状閾所を有す
為円形の外形を持−５普圧スツヌト軸受Ｋかいて。 バッキング面は環状＠所の両側に配置されている静圧ス
ラスト軸受。 ｚ パラ命ノダ薗Ｏ外径と環状開所ＯＳＳとの差は環状
凹所の値１とパラ命ング面Ｏ内後との差より大暑−轡許
請求のｌｌ１ｌ第１項のｉＩ１１１体静力学スラスト。 λ 環状１ｆｌＮ０１１１６１１１ｔＥＯ，円′ｓＭ所
ノ＠１の深さく対する比は０４か６０．６で魯ゐ特許請
求の範囲第１項ＯＩ１体曽力学スツスト軸受。[Scope of Claims] L A central circle *m*, a delivery channel s A y dP/ having a circular concavity and an Ill-shaped threshold, so it has a circular outer shape and -5 normal pressure. Use the Sunnut bearing K. The backing surface is a hydrostatic thrust bearing placed on both sides of the annular @ place. z The difference between the outer diameter of the outer diameter and the annular opening OSS is greater than the difference between the value 1 of the annular recess and the inner back of the para-indicating surface O. . λ Annular 1flN01116111tEO, the ratio of the depth of the circle'sM place @1 is 04 or 60.6.Claim 1 OI1 body dynamics strain bearing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1984582A JPS58137619A (en) | 1982-02-12 | 1982-02-12 | Static-pressure thrust bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1984582A JPS58137619A (en) | 1982-02-12 | 1982-02-12 | Static-pressure thrust bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS58137619A true JPS58137619A (en) | 1983-08-16 |
Family
ID=12010586
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1984582A Pending JPS58137619A (en) | 1982-02-12 | 1982-02-12 | Static-pressure thrust bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58137619A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4823737A (en) * | 1985-12-09 | 1989-04-25 | Hideo Nakajima | Egg transfer device |
-
1982
- 1982-02-12 JP JP1984582A patent/JPS58137619A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4823737A (en) * | 1985-12-09 | 1989-04-25 | Hideo Nakajima | Egg transfer device |
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