JP3272087B2 - Pump integrated bearing - Google Patents
Pump integrated bearingInfo
- Publication number
- JP3272087B2 JP3272087B2 JP03432093A JP3432093A JP3272087B2 JP 3272087 B2 JP3272087 B2 JP 3272087B2 JP 03432093 A JP03432093 A JP 03432093A JP 3432093 A JP3432093 A JP 3432093A JP 3272087 B2 JP3272087 B2 JP 3272087B2
- Authority
- JP
- Japan
- Prior art keywords
- pump
- retainer
- bearing
- outer ring
- annular space
- 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
Links
Landscapes
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rolling Contact Bearings (AREA)
Description
【０００１】[0001]
【産業上の利用分野】この発明は、トランスミッション
やエンジンの潤滑用および制御用オイルポンプ、あるい
は一般産業用オイルポンプ等として使用されるポンプ一
体化ベアリングに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pump integrated bearing used as an oil pump for lubrication and control of a transmission or an engine, or an oil pump for general industrial use.
【０００２】[0002]
【従来の技術】従来、オートマチックトランスミッショ
ンでは、図４に示すように主軸５１の端部近傍をケース
５２の軸受５３で支持し、軸端をオイルポンプ５４に接
続している。オイルポンプ５４は、トランスミッション
の潤滑油供給や、制御用油圧の供給に利用されるもので
あり、ギヤポンプ、トロコイドポンプ、あるいはベーン
ポンプ形式のものが使用される。軸受５３には円筒ころ
軸受、ニードル軸受、玉軸受、滑り軸受等が使用され
る。一般産業用ポンプにおいても、前記と同様に主軸の
端部近傍を軸受で支え、軸端にポンプを接続する構造が
採られる。2. Description of the Related Art Conventionally, in an automatic transmission, as shown in FIG. 4, the vicinity of the end of a main shaft 51 is supported by a bearing 53 of a case 52, and the shaft end is connected to an oil pump 54. The oil pump 54 is used for supplying lubricating oil for the transmission and for supplying hydraulic pressure for control, and a gear pump, a trochoid pump, or a vane pump is used. As the bearing 53, a cylindrical roller bearing, a needle bearing, a ball bearing, a sliding bearing, or the like is used. In general industrial pumps as well, a structure is adopted in which the vicinity of the end of the main shaft is supported by bearings and the pump is connected to the shaft end, as described above.
【０００３】[0003]
【発明が解決しようとする課題】しかし、いずれも軸受
５３とポンプ５４との２つの独立した要素部品が必要で
あり、また軸受５３とポンプ５４とが主軸５１の軸方向
に直列に配置されるため、全長が長くなってしまうとい
う問題点がある。However, each of them requires two independent element parts, the bearing 53 and the pump 54, and the bearing 53 and the pump 54 are arranged in series in the axial direction of the main shaft 51. Therefore, there is a problem that the total length becomes long.
【０００４】この発明の目的は、ポンプ要素と軸受要素
とが一体化できて、全長の短縮化、コンパクト化、およ
び軽量化が図れるポンプ一体化ベアリングを提供するこ
とである。[0004] It is an object of the present invention to provide a pump-integrated bearing in which the pump element and the bearing element can be integrated, and the overall length can be reduced, made compact, and reduced in weight.
【０００５】[0005]
【課題を解決するための手段】この発明のポンプ一体化
ベアリングは、転がり軸受の外輪にポンプハウジングを
組付けて構成される。ポンプハウジングは、保持器を内
外輪の軸心に対する偏心位置回りに回転自在に支持する
と共に、外輪と保持器との間に所定軸方向幅の環状空間
を形成する。このポンプハウジングに前記環状空間に開
通する吸入口および吐出口を設ける。保持器の周方向複
数箇所には、前記環状空間を周方向に仕切るベーンを半
径方向移動自在に設ける。A pump integrated bearing according to the present invention is constructed by assembling a pump housing with an outer ring of a rolling bearing. The pump housing rotatably supports the retainer around an eccentric position with respect to the axis of the inner and outer rings, and forms an annular space having a predetermined axial width between the outer ring and the retainer. The pump housing is provided with a suction port and a discharge port that open to the annular space. At a plurality of positions in the circumferential direction of the retainer, vanes that partition the annular space in the circumferential direction are provided so as to be movable in the radial direction.
【０００６】[0006]
【作用】この構成によると、いわゆる非平衡型ベーンポ
ンプのロータとして転がり軸受の保持器が機能し、ポン
プ作用が得られる。すなわち、内輪が回転すると、保持
器はころを介して伝わる回転力により、内輪と静止状態
の外輪との中間速度で回転する。保持器は、回転角度に
かかわらず、内外輪の軸心に対して偏心した位置にあ
り、保持器外周と外輪内周との間の環状空間は径方向幅
が円周方向に沿って次第に変化した楔状空間となってい
る。また、保持器に設けられた各ベーンは、保持器の回
転に伴う遠心力で常に外輪の内径面に押し当てられた状
態となり、前記環状空間を周方向に仕切る。そのため、
内輪の回転に伴う保持器の回転により、環状空間の各ベ
ーンで仕切られた空間が容積変化し、流体を吸入口から
環状空間に吸入して吐出口から吐出するポンプ作用を生
じる。また、このポンプ一体化ベアリングは、内外輪が
同軸で、両者の間の転動体も同軸で公転するため、転が
り軸受としての機能も得られる。According to this structure, the retainer of the rolling bearing functions as a rotor of a so-called non-equilibrium vane pump, and a pumping action is obtained. That is, when the inner race rotates, the retainer rotates at an intermediate speed between the inner race and the stationary outer race due to the rotational force transmitted through the rollers. The cage is eccentric to the axis of the inner and outer rings regardless of the rotation angle, and the annular space between the outer circumference of the cage and the inner circumference of the outer ring gradually changes in radial width along the circumferential direction. It is a wedge-shaped space. Further, each vane provided in the retainer is always pressed against the inner diameter surface of the outer ring by centrifugal force accompanying rotation of the retainer, and partitions the annular space in the circumferential direction. for that reason,
The rotation of the retainer accompanying the rotation of the inner ring changes the volume of the space partitioned by each vane in the annular space, and produces a pump action of sucking fluid from the inlet into the annular space and discharging the fluid from the outlet. In addition, in this pump integrated bearing, the inner and outer rings are coaxial, and the rolling element between the two revolves coaxially, so that a function as a rolling bearing is also obtained.
【０００７】[0007]
【実施例】この発明の一実施例を図１ないし図３に基づ
いて説明する。このポンプ一体化ベアリングは、転がり
軸受１にポンプハウジング６を組付けて構成される。転
がり軸受１は深溝玉軸受からなり、内輪２と外輪３との
間に、転動体４を保持した保持器５が介在している。シ
ャフト７は内輪２に嵌合し、スプラインまたはキー等
（図示せず）で回転方向に係止される。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described with reference to FIGS. This pump integrated bearing is configured by assembling the pump housing 6 with the rolling bearing 1. The rolling bearing 1 is made of a deep groove ball bearing, and a retainer 5 holding a rolling element 4 is interposed between the inner ring 2 and the outer ring 3. The shaft 7 is fitted to the inner race 2 and is locked in the rotation direction by a spline or a key (not shown).
【０００８】保持器５は、周方向複数箇所に転動体４を
収容するポケット１２を形成すると共に、各ポケット１
２間にベーン１６を半径方向移動自在に嵌合するベーン
ガイド孔１７を設けたリング状のものであり、断面形状
は内径側部分が幅広となったＴ字形に形成されている。
保持器５は、図２に示すように軸方向に垂直な分割面ｂ
で２分割し、両分割保持器５Ａ，５Ｂは、周方向複数箇
所に一体形成した圧入突部１８を結合溝１９に圧入させ
て互いに結合してある。突部１８および溝１９の代わり
に、ボルト・ナットで結合しても良い。保持器５を２分
割したのは軸受の組み立て上の理由からである。なお、
図２は保持器５の斜視図であるが、ポケット１２および
ベーンガイド孔１７は各々１個のみを示し、他のポケッ
ト等は図示を省略してある。保持器５の幅狭部分５ａの
幅Ｗは、ベーン１６の幅と略一致させてある。各ベーン
１６は、転動体４の直径よりも若干幅広とし、その先端
形状は外輪３の転走溝３ａの断面形状に一致させてあ
る。転動体４は、図１（Ｂ）に示した例では５個とした
が、軸受能力に合う本数とする。The cage 5 has pockets 12 for accommodating the rolling elements 4 at a plurality of positions in the circumferential direction, and each pocket 1
It is a ring-shaped member provided with a vane guide hole 17 for fitting the vane 16 between the two so as to be movable in the radial direction, and has a T-shaped cross section with a wide inner diameter portion.
As shown in FIG. 2, the retainer 5 has a dividing surface b perpendicular to the axial direction.
The two split cages 5A and 5B are connected to each other by press-fitting the press-fitting projections 18 integrally formed at a plurality of positions in the circumferential direction into the connecting grooves 19. Instead of the projection 18 and the groove 19, they may be connected by bolts and nuts. The reason why the cage 5 is divided into two parts is that the bearings are assembled. In addition,
FIG. 2 is a perspective view of the retainer 5, in which only one pocket 12 and one vane guide hole 17 are shown, and other pockets and the like are not shown. The width W of the narrow portion 5a of the retainer 5 is substantially equal to the width of the vane 16. Each vane 16 is slightly wider than the diameter of the rolling element 4, and its tip shape matches the cross-sectional shape of the rolling groove 3 a of the outer ring 3. The number of the rolling elements 4 is five in the example shown in FIG.
【０００９】図１（Ａ）において、ポンプハウジング６
は、軸方向に垂直な分割面ａで２個の分割ハウジング６
Ａ，６Ｂに分割され、互いにボルト・ナット等の締付け
具、圧入突部と溝との係合、または接着剤、溶接等によ
り接合される。外輪３は、片方の分割ハウジング６Ａに
設けられた外周壁部分１０に、圧入状態または隙間を介
して嵌合している。各分割ハウジング６Ａ，６Ｂは、外
輪１の内周面の両側縁に嵌合する環状突部１１を有し、
これら環状突部１１，１１の内径面に保持器５の両側の
幅広部分５ｂの外面が回転自在に嵌合している。環状突
部１１は、内径面の中心Ｐ（図１（Ｂ））が内輪２およ
び外輪３の軸心である軸受中心Ｏに対して所定の偏心量
ｅだけ偏心しており、したがって保持器５は前記の偏心
した中心Ｐの回りに回転自在となっている。In FIG. 1A, a pump housing 6 is shown.
Is divided into two divided housings 6 by a divided surface a perpendicular to the axial direction.
A and 6B, and are joined to each other by a fastening tool such as a bolt and a nut, engagement of a press-fitting projection with a groove, adhesive, welding, or the like. The outer ring 3 is fitted to an outer peripheral wall portion 10 provided on one of the split housings 6A via a press-fit state or a gap. Each of the split housings 6A and 6B has an annular protrusion 11 fitted to both side edges of the inner peripheral surface of the outer ring 1,
The outer surfaces of the wide portions 5b on both sides of the retainer 5 are rotatably fitted to the inner diameter surfaces of these annular projections 11,11. The annular projection 11 has its center P (FIG. 1B) of the inner diameter surface eccentric by a predetermined eccentricity e with respect to the bearing center O which is the axis of the inner ring 2 and the outer ring 3. It is rotatable around the eccentric center P.
【００１０】両分割ハウジング６Ａ，６Ｂの環状突部１
１の高さは、先端面が保持器５の幅狭部分５ａの側面お
よびベーン１６の端面に略接する高さに形成され、両分
割ハウジング６Ａ，６Ｂの取付調整により、ベーン１６
と環状突部１１との間の軸方向隙間が適量に調整され
る。したがって、両側の環状突部１１，１１と、外輪２
の内径面と、保持器５の幅狭部分５ａの外径面との間
に、閉鎖状態の環状空間１３（図１（Ｂ））が形成され
る。The annular projection 1 of the split housings 6A, 6B
The height of the first housing 1 is formed so that the front end surface thereof is substantially in contact with the side surface of the narrow portion 5a of the retainer 5 and the end surface of the vane 16, and the mounting of the split housings 6A and 6B is adjusted.
The axial gap between the annular projection 11 and the annular projection 11 is adjusted to an appropriate amount. Therefore, the annular projections 11 on both sides and the outer race 2
A closed annular space 13 (FIG. 1B) is formed between the inner diameter surface of the holder 5 and the outer diameter surface of the narrow portion 5a of the retainer 5.
【００１１】環状空間１３は、保持器５の偏心により、
円周方向に漸次狭まった楔状の空間となり、かつ各ベー
ン１６で円周方向に仕切られている。この環状空間１３
に対して吸入口８と吐出口９とが、片方の分割ハウジン
グ６Ａに環状突部１１を貫通して形成されている。吸入
口８と吐出口９とは、各々環状突部１１の略半周にわた
る円弧状のスリットに形成され（図３）、かつスリット
幅が環状突部１１の内径面の偏心側に漸次狭くなるよう
に形成されている。Due to the eccentricity of the retainer 5, the annular space 13
It becomes a wedge-shaped space gradually narrowing in the circumferential direction, and is partitioned in the circumferential direction by each vane 16. This annular space 13
In contrast, a suction port 8 and a discharge port 9 are formed in one of the split housings 6A so as to pass through the annular projection 11. The suction port 8 and the discharge port 9 are each formed in an arc-shaped slit extending over substantially half the circumference of the annular projection 11 (FIG. 3), and the slit width is gradually narrowed toward the eccentric side of the inner diameter surface of the annular projection 11. Is formed.
【００１２】この構成によると、次のように非平衡型の
ベーンポンプとして動作する。すなわち、シャフト７が
回転し、シャフト７と一体の内輪２が回転すると、保持
器５は転動体４を介して伝わる回転力により、内輪２と
静止状態の外輪３との中間速度で回転する。保持器５
は、回転角度にかかわらず、内外輪２，３の軸心Ｏに対
して偏心した位置にあり、保持器５と外輪２との間の環
状空間１３は径方向幅が円周方向に次第に変化する楔状
空間となっている。また、保持器５に設けられた各ベー
ン１６は、保持器５の回転に伴う遠心力で常に外輪３の
内径面に押し当てられた状態となり、環状空間１３を周
方向に仕切る。そのため、内輪２の回転に伴う保持器５
の回転により、環状空間１３の各ベーンで仕切られた空
間が容積変化し、ポンプ作用を生じる。すなわち、吸入
口８から吸入されたオイル等の流体が環状空間１３を経
て吐出口９から吐出される。According to this configuration, it operates as a non-equilibrium vane pump as follows. That is, when the shaft 7 rotates and the inner race 2 integral with the shaft 7 rotates, the retainer 5 rotates at an intermediate speed between the inner race 2 and the stationary outer race 3 by the rotational force transmitted through the rolling elements 4. Cage 5
Is located eccentrically with respect to the axis O of the inner and outer rings 2, 3 regardless of the rotation angle, and the annular space 13 between the retainer 5 and the outer ring 2 gradually changes in radial width in the circumferential direction. It is a wedge-shaped space. In addition, each vane 16 provided in the retainer 5 is constantly pressed against the inner diameter surface of the outer ring 3 by centrifugal force accompanying the rotation of the retainer 5, and partitions the annular space 13 in the circumferential direction. Therefore, the retainer 5 accompanying the rotation of the inner ring 2
Due to the rotation of the space, the volume of the space partitioned by the vanes of the annular space 13 changes, and a pump action occurs. That is, fluid such as oil sucked from the suction port 8 is discharged from the discharge port 9 through the annular space 13.
【００１３】吐出量は次式のようになる。 Ｄ＝４πＲｂｅ−ｎｔｂｅ−ｎ′Ｖｅ ここで、Ｄ；１回転当たりの吐出量 Ｒ；外輪の転走溝平均深さにおける半径 ｂ；ベーン軸方向幅 ｅ；偏心量 ｎ；ベーン数 ｔ；ベーン厚さ ｎ′；転動体数 Ｖ；転動体容積The discharge amount is given by the following equation. D = 4πRbe-ntbe-n′Ve Here, D: discharge amount per rotation R: radius of the outer ring at the average rolling groove depth b: vane axial width e; eccentricity n: vane number t: vane thickness N ': number of rolling elements V: volume of rolling elements
【００１４】また、このポンプ一体化ベアリングは、内
外輪２，３が同軸であり、両者の間の転動体４も同軸で
公転するため、通常の転がり軸受としても機能する。こ
のポンプ一体化ベアリングは、このようにポンプ機能お
よび軸受機能が得られ、これをトランスミッションや、
エンジンのポンプ、あるいは一般用ポンプとして使う場
合に、軸受とポンプとの一体化により、全長が短縮化さ
れる。また、ポンプハウジング６が軸受のハウジングを
兼用し、かつ保持器５がベーン１６を回転させるロータ
を兼用することになり、全体がコンパクト化されて軽量
化される。The pump integrated bearing also functions as a normal rolling bearing because the inner and outer races 2 and 3 are coaxial and the rolling element 4 between them revolves coaxially. In this pump integrated bearing, a pump function and a bearing function are obtained as described above.
When used as an engine pump or a general-purpose pump, the overall length is reduced by integrating the bearing with the pump. In addition, the pump housing 6 also serves as a housing for bearings, and the retainer 5 also serves as a rotor for rotating the vanes 16, so that the whole is reduced in size and weight.
【００１５】なお、前記実施例は転がり軸受１が深溝玉
軸受である場合につき説明したが、転がり軸受１には円
筒ころ軸受や円すいころ軸受等、各種の転がり軸受が使
用できる。円筒ころ軸受を使用する場合は、ベーン１６
の外径端は外輪の内径面に沿う直線形状のものとでき
る。Although the above embodiment has been described with reference to the case where the rolling bearing 1 is a deep groove ball bearing, various rolling bearings such as a cylindrical roller bearing and a tapered roller bearing can be used as the rolling bearing 1. When using a cylindrical roller bearing, the vane 16
Can have a linear shape along the inner diameter surface of the outer ring.
【００１６】[0016]
【発明の効果】この発明のポンプ一体化ベアリングは、
転がり軸受の外輪にポンプハウジングを組付け、このポ
ンプハウジングにより保持器を偏心位置で回転自在に支
持して外輪と保持器との間に半径方向幅が次第に変化す
る環状空間を形成し、かつ前記保持器にベーンを取付け
たものであるため、内輪の回転に伴う保持器の回転でベ
ーンが公転し、ポンプ作用が得られる。そのため、ポン
プ要素と軸受要素とが一体化された装置となり、軸受お
よびポンプを独立して設けたものに比べて、全長が短
く、コンパクトな構成で、軽量化が可能なものとなる。The pump integrated bearing of the present invention is
A pump housing is assembled to the outer ring of the rolling bearing, and the pump housing rotatably supports the retainer at an eccentric position to form an annular space between the outer ring and the retainer in which the radial width gradually changes, and Since the vane is attached to the retainer, the vane revolves due to the rotation of the retainer accompanying the rotation of the inner ring, and a pump action is obtained. For this reason, a device in which the pump element and the bearing element are integrated is provided, and compared with a device in which the bearing and the pump are independently provided, the overall length is shorter, the configuration is compact, and the weight can be reduced.
【図１】（Ａ）はこの発明の一実施例の破断側面図、
（Ｂ）は同図（Ａ）のＢ−Ｂ線断面図である。FIG. 1A is a cutaway side view of one embodiment of the present invention;
(B) is a sectional view taken along line BB of FIG.
【図２】保持器の概略斜視図である。FIG. 2 is a schematic perspective view of a retainer.
【図３】図１（Ａ）のＣ−Ｃ線断面において、環状突部
のみを示した断面図である。FIG. 3 is a cross-sectional view showing only an annular protrusion in a cross section taken along line CC of FIG. 1 (A).
【図４】従来例の破断側面図である。FIG. 4 is a cutaway side view of a conventional example.
１…転がり軸受、２…内輪、３…外輪、４…転動体、５
…保持器、６…ポンプハウジング、６Ａ，６Ｂ…分割ハ
ウジング、７…シャフト、８…吸入口、９…吐出口、１
３…環状空間、１６…ベーンDESCRIPTION OF SYMBOLS 1 ... Rolling bearing, 2 ... Inner ring, 3 ... Outer ring, 4 ... Rolling element, 5
... Cage, 6 ... Pump housing, 6A, 6B ... Split housing, 7 ... Shaft, 8 ... Suction port, 9 ... Discharge port, 1
3 ... Annular space, 16 ... Vane
───────────────────────────────────────────────────── フロントページの続き (58)調査した分野(Int.Cl.7，ＤＢ名) F04C 15/00 F04C 2/344 331 F16C 19/00 F16C 33/38 F16C 33/46 ──────────────────────────────────────────────────続 き Continuation of front page (58) Field surveyed (Int. Cl. 7 , DB name) F04C 15/00 F04C 2/344 331 F16C 19/00 F16C 33/38 F16C 33/46
Claims (1)
を内外輪の軸心に対する偏心位置回りに回転自在に支持
すると共に、外輪と保持器との間に所定軸方向幅の環状
空間を形成するポンプハウジングを設け、このポンプハ
ウジングに前記環状空間に開通する吸入口および吐出口
を設け、前記保持器の周方向複数箇所に、前記環状空間
を周方向に仕切るベーンを半径方向移動自在に設けたポ
ンプ一体化ベアリング。1. A rolling bearing which is assembled to an outer ring of a rolling bearing to rotatably support a retainer around an eccentric position with respect to an axis of an inner and outer ring, and forms an annular space having a predetermined axial width between the outer ring and the retainer. A pump housing is formed, and the pump housing is provided with an inlet port and a discharge port that open to the annular space, and vanes that partition the annular space in the circumferential direction at a plurality of locations in the circumferential direction of the retainer are movable in the radial direction. Pump integrated bearing provided.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP03432093A JP3272087B2 (en) | 1993-01-29 | 1993-01-29 | Pump integrated bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP03432093A JP3272087B2 (en) | 1993-01-29 | 1993-01-29 | Pump integrated bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH06221276A JPH06221276A (en) | 1994-08-09 |
| JP3272087B2 true JP3272087B2 (en) | 2002-04-08 |
Family
ID=12410876
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP03432093A Expired - Fee Related JP3272087B2 (en) | 1993-01-29 | 1993-01-29 | Pump integrated bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3272087B2 (en) |
-
1993
- 1993-01-29 JP JP03432093A patent/JP3272087B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH06221276A (en) | 1994-08-09 |
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