JPS6224059Y2 - - Google Patents
Info
- Publication number
- JPS6224059Y2 JPS6224059Y2 JP1979024085U JP2408579U JPS6224059Y2 JP S6224059 Y2 JPS6224059 Y2 JP S6224059Y2 JP 1979024085 U JP1979024085 U JP 1979024085U JP 2408579 U JP2408579 U JP 2408579U JP S6224059 Y2 JPS6224059 Y2 JP S6224059Y2
- Authority
- JP
- Japan
- Prior art keywords
- sliding
- recess
- shoe
- sliding shoe
- groove
- 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
- 238000003754 machining Methods 0.000 claims 1
- 230000001154 acute effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 125000006850 spacer group Chemical group 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
Landscapes
- Reciprocating Pumps (AREA)
- Hydraulic Motors (AREA)
Description
【考案の詳細な説明】
この考案は、ラジアルピストン機械、特に高速
用のラジアル油圧ポンプ・モータに適する滑りシ
ユーに関するものである。DETAILED DESCRIPTION OF THE INVENTION This invention relates to a sliding shoe suitable for radial piston machines, especially high-speed radial hydraulic pump motors.
つぎに、従来のラジアル油圧ポンプ・モータの
滑りシユーの例を、第１図ないし第４図により説
明する。 Next, an example of a sliding shoe of a conventional radial hydraulic pump/motor will be explained with reference to FIGS. 1 to 4.
入（出）力軸（図示してない）に結合されたロ
ータ１には、複数個（ただし、図には一つしか表
してない）のシリンダ２が間隔をおいて放射状に
設けられており、各シリンダ２にはピストン３が
おさめられており、ピストン３には矩形状の滑り
底５をそなえた滑りシユー４の球状部がスペーサ
６、リング７により揺動可能に取付けられてい
る。滑りシユー４の滑り底５は、ロータ１の回転
にともなつてカムリング８の内周面８ａを摺動す
る。 A rotor 1 connected to an input (output) shaft (not shown) has a plurality of cylinders 2 (however, only one is shown in the figure) arranged radially at intervals. A piston 3 is housed in each cylinder 2, and a spherical part of a sliding shoe 4 having a rectangular sliding bottom 5 is swingably attached to the piston 3 by a spacer 6 and a ring 7. The sliding bottom 5 of the sliding shoe 4 slides on the inner peripheral surface 8a of the cam ring 8 as the rotor 1 rotates.
滑りシユー４の滑り底５にはカムリング８に対
向させる円形（第２図、第３図参照）またはほぼ
正方形（第４図参照）の凹部９が設けられてお
り、この凹部９は滑りシユー４の軸線方向に設け
た通路１０につらねられている。滑り底５の凹部
９のまわりには一定幅のシールウエーブ１１が形
成されており、外側には摺動面１２ａ，１２ｂが
形成されている。シールウエーブ１１と摺動面１
２ａ，１２ｂとは、カムリング８に対してほぼ直
角に近い角度で縦掘りした溝１３で区画されてい
る。 The sliding bottom 5 of the sliding shoe 4 is provided with a circular (see FIGS. 2 and 3) or approximately square (see FIG. 4) recess 9 that faces the cam ring 8. It is suspended in a passage 10 provided in the axial direction. A seal wave 11 of a constant width is formed around the recess 9 of the sliding sole 5, and sliding surfaces 12a and 12b are formed on the outside. Seal wave 11 and sliding surface 1
2a and 12b are separated by a groove 13 cut vertically at an angle almost perpendicular to the cam ring 8.
ピストン３の上側部に導びかれた圧油は、通路
１０を経て凹部９にはいり、滑り底５とカムリン
グ８との間で静圧的な釣合いがとられる。また、
摺動面１２ａ，１２ｂとカムリング８との間で
は、動圧的な圧力面を形成し、ピストン３を介し
て滑りシユー４にかかる負荷に耐える能力、すな
わち滑りシユー４の負荷能力を高める。 The pressure oil guided to the upper side of the piston 3 enters the recess 9 through the passage 10, and static pressure is balanced between the sliding bottom 5 and the cam ring 8. Also,
A dynamic pressure surface is formed between the sliding surfaces 12a, 12b and the cam ring 8, increasing the ability to withstand the load applied to the sliding shoe 4 via the piston 3, that is, the load capacity of the sliding shoe 4.
上述の滑りシユー４では、溝１３の摺動面１２
ａ，１２ｂ側における端面１４が、カムリング８
の内周面にほぼ直角となり、回転時に動圧を発生
させようとする油を摺動方向の両側にかき出して
しまい、動圧による滑りシユー４の負荷能力を低
下する。この対策として溝１３の端面１４を面取
りしているが、精度良く面取りすることは難しく
時間がかかり、原価高を招く。 In the sliding shoe 4 described above, the sliding surface 12 of the groove 13
The end face 14 on the a, 12b side is the cam ring 8
The sliding shoe 4 is substantially perpendicular to the inner circumferential surface of the sliding shoe 4, and when it rotates, the oil that tends to generate dynamic pressure is scraped out to both sides in the sliding direction, reducing the load capacity of the sliding shoe 4 due to the dynamic pressure. As a countermeasure to this problem, the end face 14 of the groove 13 is chamfered, but chamfering with high precision is difficult and takes time, leading to an increase in cost.
この考案は上記の欠点を除くためのもので、滑
り底に油をかき出すことのない溝を設けることに
より、動圧的な圧力面を形成し、滑りシユーの負
荷能力の増大をはかつたものである。 This idea was created to eliminate the above-mentioned drawbacks, and by providing a groove in the bottom of the slide that does not scrape out oil, a dynamic pressure surface is formed and the load capacity of the slide shoe is increased. It is.
以下、この考案の一実施態様を第５図および第
６図により説明する。両図において、第１図およ
び第３図と同じ符号をつけたものは同じものもし
くは相当するものを表わす。 An embodiment of this invention will be described below with reference to FIGS. 5 and 6. In both figures, the same reference numerals as in FIGS. 1 and 3 represent the same or equivalent elements.
溝１５の底面はシールウエーブ１１の外側にお
いて、滑り底５の先端からｈの寸法の平面１５ａ
で形成されている。この結果、摺動面１２ａ，１
２ｂの内側の境界線１６は、カムリング８とその
軸心に平行な平面との交線になり、いいかえれば
滑りシユー４の摺動方向と直角な直線となる。溝
１５の前記寸法ｈを変化させることにより、摺動
面１２ａ，１２ｂの巾も任意に選ぶことができ
る。 The bottom surface of the groove 15 is a plane 15a with a dimension h from the tip of the sliding bottom 5 on the outside of the seal wave 11.
It is formed of. As a result, the sliding surfaces 12a, 1
The inner boundary line 16 of 2b is a line of intersection between the cam ring 8 and a plane parallel to its axis, or in other words, a straight line perpendicular to the sliding direction of the sliding shoe 4. By changing the dimension h of the groove 15, the widths of the sliding surfaces 12a and 12b can also be arbitrarily selected.
以上説明したこの考案の滑りシユーでは、摺動
面１２ａ，１２ｂの溝１５側の端縁がカムリング
８に対して鋭角的に接するので、油をまき込みや
すく、動圧が発生しやすい。また、摺動面１２
ａ，１２ｂが摩耗した場合、それは見かけ上第５
図の寸法ｈが縮小したと同じことになり、その結
果、摺動面１２ａ，１２ｂの巾が増大し、負荷能
力が増加する。したがつて、摺動面１２ａ，１２
ｂの摩耗の進行を遅らせる効果も得られる。 In the above-described sliding shoe of this invention, the edges of the sliding surfaces 12a, 12b on the groove 15 side contact the cam ring 8 at an acute angle, so oil is easily drawn in and dynamic pressure is easily generated. In addition, the sliding surface 12
When a and 12b are worn out, it appears that the fifth
This is the same as reducing the dimension h in the figure, and as a result, the widths of the sliding surfaces 12a, 12b increase and the load capacity increases. Therefore, the sliding surfaces 12a, 12
The effect of delaying the progress of wear b can also be obtained.
第１図は従来の滑りシユーをそなえたラジアル
油圧ポンプの一例を示す断面側面図、第２図、第
３図、第４図は従来の滑りシユーを示す底面図、
第５図はこの考案の一実施態様を示す断面側面
図、第６図は第５図の滑りシユーの底面図であ
る。
１……ロータ、２……シリンダ、３……ピスト
ン、４……滑りシユー、５……滑り底、８……カ
ムリング、９……凹部、１０……通路、１１……
シールウエーブ、１２ａ，１２ｂ……摺動面、１
５……溝、１６……境界線。
FIG. 1 is a cross-sectional side view showing an example of a radial hydraulic pump equipped with a conventional sliding shoe; FIGS. 2, 3, and 4 are bottom views showing conventional sliding shoes;
FIG. 5 is a sectional side view showing one embodiment of this invention, and FIG. 6 is a bottom view of the sliding shoe shown in FIG. 1... Rotor, 2... Cylinder, 3... Piston, 4... Sliding shoe, 5... Sliding bottom, 8... Cam ring, 9... Recess, 10... Passage, 11...
Seal wave, 12a, 12b...sliding surface, 1
5...Groove, 16...Boundary line.
Claims (1)
動面８ａに沿つて運動するほぼ矩形状の滑り底５
をそなえ、その滑り底５に、一つの凹部９と複数
の摺動面１２ａ，１２ｂとを形成し、凹部９に通
路１０を介して圧力媒体が供給されるように構成
したラジアルピストン機械用滑りシユーにおい
て、凹部９を一定幅のシールウエーブ１１により
囲み、シールウエーブ１１の外周の溝１５の加工
深さｈにより決まる平面１５ａと滑り底５の摺動
する円筒形の摺動面８ａとの交わる線により、複
数の摺動面の範囲を形成したことを特徴とするラ
ジアルピストン機械用滑りシユー。 A substantially rectangular sliding bottom 5 that moves along a cylindrical sliding surface 8a formed on a member 8 that provides stroke motion.
A slide for a radial piston machine, which has a recess 9 and a plurality of sliding surfaces 12a, 12b formed in the slide bottom 5, and is configured such that a pressure medium is supplied to the recess 9 through a passage 10. In the shoe, the recess 9 is surrounded by a seal wave 11 of a constant width, and a plane 15a determined by the machining depth h of the groove 15 on the outer periphery of the seal wave 11 intersects with the cylindrical sliding surface 8a on which the sliding bottom 5 slides. A sliding shoe for a radial piston machine, characterized in that a plurality of sliding surface ranges are formed by lines.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1979024085U JPS6224059Y2 (en) | 1979-02-28 | 1979-02-28 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1979024085U JPS6224059Y2 (en) | 1979-02-28 | 1979-02-28 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS55125979U JPS55125979U (en) | 1980-09-06 |
| JPS6224059Y2 true JPS6224059Y2 (en) | 1987-06-19 |
Family
ID=28861896
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1979024085U Expired JPS6224059Y2 (en) | 1979-02-28 | 1979-02-28 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6224059Y2 (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS519924A (en) * | 1974-07-16 | 1976-01-27 | Toppan Moore Kk | Kumichohyono seizohoho |
| JPS5566672A (en) * | 1978-11-11 | 1980-05-20 | Bosch Gmbh Robert | Sliding shoe for hydrostatic piston machine |
-
1979
- 1979-02-28 JP JP1979024085U patent/JPS6224059Y2/ja not_active Expired
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS519924A (en) * | 1974-07-16 | 1976-01-27 | Toppan Moore Kk | Kumichohyono seizohoho |
| JPS5566672A (en) * | 1978-11-11 | 1980-05-20 | Bosch Gmbh Robert | Sliding shoe for hydrostatic piston machine |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS55125979U (en) | 1980-09-06 |
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