JP2017031879A - Lubrication pump - Google Patents
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Abstract
Description
本発明は、潤滑ポンプに関する。 The present invention relates to a lubrication pump.
例えば、摩擦ローラ式減速機においては、サンローラ、中間ローラ、リングローラ等の各ローラが高速回転して使用されため、各ローラを回転自在に支持する軸受や、各ローラのトラクション面の潤滑状態を良好に維持する必要がある。このようなトラクション面に潤滑油を供給するポンプとして、中間ローラの外周面に螺旋溝を設け、この螺旋溝によりハウジングの下部に存在する潤滑油、及び浮遊するミスト状の潤滑油を取り込んで、トラクション面を潤滑するようにした摩擦ローラ式減速機が知られている(例えば、特許文献1参照)。また、出力軸と同軸にトロコイドポンプを設け、このトロコイドポンプによりハウジング内に存在する潤滑油を各部に給油するようにした摩擦ローラ式減速機も知られている(例えば、特許文献2参照)。 For example, in a friction roller type speed reducer, since each roller such as a sun roller, an intermediate roller, and a ring roller rotates at high speed, the lubrication state of a bearing that rotatably supports each roller and the traction surface of each roller is determined. It needs to be maintained well. As a pump for supplying lubricating oil to such a traction surface, a spiral groove is provided on the outer peripheral surface of the intermediate roller, and by this spiral groove, the lubricating oil present in the lower part of the housing and the floating mist-like lubricating oil are taken in, A friction roller type speed reducer that lubricates a traction surface is known (see, for example, Patent Document 1). There is also known a friction roller type speed reducer in which a trochoid pump is provided coaxially with the output shaft, and lubricating oil present in the housing is supplied to each part by this trochoid pump (see, for example, Patent Document 2).
ところが、特許文献1に記載の摩擦ローラ式減速機では、中間ローラの外周面に形成された螺旋溝から離れた位置への給油がし難いという問題があった。また、特許文献2に記載のトロコイドポンプは、容積型ポンプであり、回転数の増加と共に内部が高圧になって駆動トルクが線形的に増加する。このようなポンプが、非常に高速で駆動される摩擦ローラ式減速機の出力軸に配置されると、摩擦ローラ式減速機全体の駆動トルクに占めるポンプの駆動トルクの割合が、高速回転時、或いは急加減速時に大きくなり過ぎるという問題があった。 However, the friction roller type speed reducer described in Patent Document 1 has a problem that it is difficult to supply oil to a position away from the spiral groove formed on the outer peripheral surface of the intermediate roller. Moreover, the trochoid pump described in Patent Document 2 is a positive displacement pump, and the internal torque becomes high as the number of rotations increases, and the drive torque increases linearly. When such a pump is arranged on the output shaft of a friction roller type speed reducer driven at a very high speed, the ratio of the pump driving torque to the driving torque of the entire friction roller type speed reducer is as follows: Or there was a problem that it became too large during sudden acceleration / deceleration.
本発明は、上述した事情に鑑みてなされたものであり、その目的は、外部に潤滑ポンプを特別に設けることなく、例えば、摩擦ローラ式減速機等の高い吐出圧を要しない摺動部に潤滑油を安定して供給することができる、低駆動トルク、且つ小型の潤滑ポンプを提供することにある。 The present invention has been made in view of the above-described circumstances, and its object is to provide a sliding portion that does not require a high discharge pressure, such as a friction roller type speed reducer, without specially providing a lubrication pump outside. An object of the present invention is to provide a small-sized lubrication pump having a low driving torque and capable of stably supplying lubricating oil.
本発明は下記構成からなる。
(1)内輪、外輪、及び前記内輪と前記外輪との間の軸受内部空間における軸方向一端側に、転動自在に複数の転動体が配置された転がり軸受と、
前記軸受内部空間の軸方向他端側に設けられ、潤滑油を前記軸受内部空間と軸受外部との間で吸引及び吐出可能なポンプ部と、
前記ポンプ部の軸方向両側の前記内輪と前記外輪との間に配置された封止部材と、
を備え、
前記ポンプ部は、
前記内輪に外嵌される円環状のインペラベースの外周面に、周方向に亘って複数の羽根部が形成されたインペラと、
前記外輪に内嵌されて前記インペラと協働してポンプ室を構成すると共に、前記ポンプ室を吸込み側と吐出側とに分離するステータと、
を備え、
前記外輪は、前記ポンプ室の前記吸込み側と軸受外部とを接続する複数の吸入孔と、前記ポンプ室の前記吐出側と前記軸受外部とを接続する複数の吐出孔とが形成されていることを特徴とする潤滑ポンプ。
(2)前記複数の吸入孔は、前記外輪の外周面に円周方向に沿って形成された外周側リセス溝に開口することを特徴とする上記(1)に記載の潤滑ポンプ。
(3)前記複数の吐出孔は、前記外輪の内周面に円周方向に沿って形成された内周側リセス溝に開口することを特徴とする上記(1)又は(2)に記載の潤滑ポンプ。
The present invention has the following configuration.
(1) An inner ring, an outer ring, and a rolling bearing in which a plurality of rolling elements are arranged so as to roll freely on one end side in the axial direction in the bearing inner space between the inner ring and the outer ring,
A pump portion provided on the other axial end side of the bearing internal space, and capable of sucking and discharging the lubricating oil between the bearing internal space and the outside of the bearing;
A sealing member disposed between the inner ring and the outer ring on both axial sides of the pump part;
With
The pump part is
An impeller having a plurality of blade portions formed on the outer circumferential surface of an annular impeller base fitted to the inner ring over the circumferential direction;
A stator that is fitted into the outer ring and forms a pump chamber in cooperation with the impeller, and separates the pump chamber into a suction side and a discharge side;
With
The outer ring is formed with a plurality of suction holes that connect the suction side of the pump chamber and the outside of the bearing, and a plurality of discharge holes that connect the discharge side of the pump chamber and the outside of the bearing. Lubricating pump characterized by
(2) The lubrication pump according to (1), wherein the plurality of suction holes are opened in an outer peripheral recess groove formed in an outer peripheral surface of the outer ring along a circumferential direction.
(3) In the above (1) or (2), the plurality of discharge holes open in an inner circumferential recess groove formed along the circumferential direction on the inner circumferential surface of the outer ring. Lubrication pump.
本発明の潤滑ポンプによれば、外部に潤滑ポンプを特別に設けることなく、低駆動トルク、且つ小型化された潤滑ポンプにより、高い吐出圧を要しない摺動部に潤滑油を安定して供給することができる。 According to the lubricating pump of the present invention, the lubricating oil can be stably supplied to the sliding portion that does not require a high discharge pressure by the low-torque torque and the miniaturized lubricating pump without providing a special lubricating pump outside. can do.
以下、本発明に係る潤滑ポンプの好適な実施の形態について、図面を参照して詳細に説明する。
図1は潤滑ポンプの外観を示す側面図、図2は潤滑ポンプの分解斜視図、図3は図1のA−A線断面図、図4は図3に示す潤滑ポンプの要部拡大図である。
Hereinafter, preferred embodiments of a lubrication pump according to the present invention will be described in detail with reference to the drawings.
1 is a side view showing the appearance of the lubrication pump, FIG. 2 is an exploded perspective view of the lubrication pump, FIG. 3 is a sectional view taken along line AA in FIG. 1, and FIG. 4 is an enlarged view of the main part of the lubrication pump shown in FIG. is there.
図1〜図4に示す潤滑ポンプ100は、軌道輪が軸方向に延設された転がり軸受20の内部に、ポンプ部50が一体に組み付けられた構成を有する。また、本構成の転がり軸受20としては、単列の深溝玉軸受を例示している。 The lubricating pump 100 shown in FIGS. 1-4 has the structure by which the pump part 50 was integrally assembled | attached inside the rolling bearing 20 by which the bearing ring was extended in the axial direction. Moreover, as the rolling bearing 20 of this structure, the single row deep groove ball bearing is illustrated.
転がり軸受20は、図3に示すように、内輪21と、外輪25と、転動体としての複数の玉29とを有する。内輪21は、外周面に一条の内輪軌道23が形成される。外輪25は、内周面に一条の外輪軌道27が形成される。複数の玉29は、保持器31に保持された状態で、内輪軌道23と外輪軌道27との間に転動自在に配置される。 As shown in FIG. 3, the rolling bearing 20 includes an inner ring 21, an outer ring 25, and a plurality of balls 29 as rolling elements. The inner ring 21 has a single inner ring raceway 23 formed on the outer peripheral surface. The outer ring 25 has a single outer ring raceway 27 formed on the inner peripheral surface. The plurality of balls 29 are arranged between the inner ring raceway 23 and the outer ring raceway 27 so as to roll freely while being held by the cage 31.
複数の玉29は、内輪21と外輪25との間の軸受内部空間Sにおける軸方向一端側に配置される。また、軸受内部空間Sにおける軸方向他端側には、潤滑油を軸受内部空間Sと軸受外部との間で吸引及び吐出可能なポンプ部50が配置される。 The plurality of balls 29 are arranged on one end side in the axial direction in the bearing inner space S between the inner ring 21 and the outer ring 25. Further, on the other end side in the axial direction of the bearing internal space S, a pump unit 50 capable of sucking and discharging the lubricating oil between the bearing internal space S and the outside of the bearing is disposed.
ポンプ部50は、図2に示すように、円環状のインペラ51と、ステータ53とを備える。インペラ51は、図3に示すように、内輪21の外周面21aに外嵌固定される。ステータ53は、外輪25の内周面25aに内嵌固定される。このポンプ部50が配置される軸受内部空間Sの軸方向両側には、一対の封止部材61,62が配置される。 As shown in FIG. 2, the pump unit 50 includes an annular impeller 51 and a stator 53. As shown in FIG. 3, the impeller 51 is externally fitted and fixed to the outer peripheral surface 21 a of the inner ring 21. The stator 53 is fitted and fixed to the inner peripheral surface 25 a of the outer ring 25. A pair of sealing members 61 and 62 are disposed on both sides in the axial direction of the bearing internal space S where the pump unit 50 is disposed.
インペラ51は、図2に示すように、円環状のインペラベース51aと、インペラベース51aに周方向に亘って接続される複数の羽根部5bとを有する。これらインペラベース51aと羽根部51bは、樹脂材料等により一体に成形される。羽根部51bの形状は、所謂、斜流形の羽根形状となっている。 As shown in FIG. 2, the impeller 51 includes an annular impeller base 51a and a plurality of blade portions 5b connected to the impeller base 51a in the circumferential direction. The impeller base 51a and the blade portion 51b are integrally formed of a resin material or the like. The shape of the blade portion 51b is a so-called mixed flow blade shape.
ステータ53は、図4に示すように、インペラ51の径方向外側に、羽根部51bの外縁形状に沿わせて対向して配置される。これにより、ステータ53は、インペラ51と協働してポンプ室55を構成する。また、ステータ53は、ポンプ室55を吸込み側ポンプ室55aと吐出側ポンプ室55bとに分離する。ステータ53には、吸込み側ポンプ室55a側に、潤滑油を吸入するための径方向に貫通する複数の孔57が、周方向に沿って等間隔で形成される。 As shown in FIG. 4, the stator 53 is disposed on the radially outer side of the impeller 51 so as to face the outer edge shape of the blade portion 51 b. As a result, the stator 53 forms a pump chamber 55 in cooperation with the impeller 51. The stator 53 separates the pump chamber 55 into a suction side pump chamber 55a and a discharge side pump chamber 55b. In the stator 53, a plurality of holes 57 penetrating in the radial direction for sucking lubricating oil are formed at equal intervals along the circumferential direction on the suction side pump chamber 55a side.
外輪25には、吸込み側ポンプ室55aに対応する軸方向位置に、周方向に沿って等間隔で、複数の吸入孔33が径方向に貫通して形成される(図2参照)。これらの吸入孔33は、吸込み側ポンプ室55aと軸受外部とを連通させる。外輪25の外周面には、円周方向に沿って外周側リセス溝35が形成される。この外周側リセス溝35の溝底部に、複数の吸入孔33が開口する。 The outer ring 25 is formed with a plurality of suction holes 33 penetrating in the radial direction at equal intervals along the circumferential direction at axial positions corresponding to the suction-side pump chamber 55a (see FIG. 2). These suction holes 33 allow the suction side pump chamber 55a to communicate with the outside of the bearing. An outer peripheral recess groove 35 is formed on the outer peripheral surface of the outer ring 25 along the circumferential direction. A plurality of suction holes 33 are opened at the groove bottom of the outer peripheral recess groove 35.
また、外輪25には、吐出側ポンプ室55bに対応する軸方向位置に、周方向に沿って等間隔に、複数の吐出孔37が径方向に貫通して形成される。これらの吐出孔37は、吐出側ポンプ室55bと軸受外部とを連通させる。また、外輪25の内周面には、円周方向に沿って内周側リセス溝39が形成される。複数の吐出孔37は、この内周側リセス溝39に開口している。内周側リセス溝39は、渦巻きポンプにおけるケーシングと同様に、潤滑油が通過する間に速度エネルギを効率よく圧力エネルギに変換する効果を発揮する。 The outer ring 25 is formed with a plurality of discharge holes 37 penetrating in the radial direction at equal intervals along the circumferential direction at axial positions corresponding to the discharge-side pump chamber 55b. These discharge holes 37 allow the discharge-side pump chamber 55b to communicate with the outside of the bearing. An inner peripheral recess groove 39 is formed on the inner peripheral surface of the outer ring 25 along the circumferential direction. The plurality of discharge holes 37 are open to the inner peripheral recess groove 39. The inner peripheral recess groove 39 exhibits an effect of efficiently converting velocity energy into pressure energy while the lubricating oil passes, like the casing in the spiral pump.
一対の封止部材61,62は、図3に示すように、ポンプ部50の軸方向両側の内輪21と外輪25との間に配置される。すなわち、転がり軸受20の玉29とポンプ部50との間に封止部材61が配置され、ポンプ部50の玉29とは反対側の端部に封止部材62が配置される。一対の封止部材61,62は、図4に示すように、断面略L字形の円環状に形成された芯金63と、耐油性ゴムで形成されて芯金63に固着された弾性シール体65と、からなる。弾性シール体65には、内輪21及びインペラ51に摺接する一対のリップ部65a,65bが形成される。 As shown in FIG. 3, the pair of sealing members 61 and 62 are disposed between the inner ring 21 and the outer ring 25 on both sides in the axial direction of the pump unit 50. That is, the sealing member 61 is disposed between the ball 29 of the rolling bearing 20 and the pump unit 50, and the sealing member 62 is disposed at the end of the pump unit 50 opposite to the ball 29. As shown in FIG. 4, the pair of sealing members 61 and 62 includes a cored bar 63 formed in an annular shape having a substantially L-shaped cross section, and an elastic seal body formed of oil-resistant rubber and fixed to the cored bar 63. 65. The elastic seal body 65 is formed with a pair of lip portions 65 a and 65 b that are in sliding contact with the inner ring 21 and the impeller 51.
一対の封止部材61,62は、外周が外輪25の内周面に形成されたシール装着溝41に圧入され、リップ部65aがインペラ51の軸方向一端部、リップ部65bが内輪21のシール溝43にそれぞれ摺接する。これにより、内輪21と外輪25との間を封止している。つまり、封止部材61a,61bは、ポンプ部50から軸受外部に潤滑油が漏れないように、且つ、外部からポンプ部50に塵埃が入り込まないように封止している。 The pair of sealing members 61, 62 is press-fitted into a seal mounting groove 41 having an outer periphery formed on the inner peripheral surface of the outer ring 25, the lip portion 65 a is one end in the axial direction of the impeller 51, and the lip portion 65 b is a seal of the inner ring 21. Each is in sliding contact with the groove 43. Thereby, the space between the inner ring 21 and the outer ring 25 is sealed. That is, the sealing members 61a and 61b are sealed so that the lubricating oil does not leak from the pump unit 50 to the outside of the bearing and dust does not enter the pump unit 50 from the outside.
図5は、潤滑ポンプがハウジング71に組み込まれた状態の図3におけるB−B線断面図である。
上記構成の潤滑ポンプ100は、ハウジング71に形成された軸受孔73に外輪25が圧入されると共に、不図示の回転軸が内輪21に挿通される。なお、潤滑ポンプ100から供給される潤滑油は、自重により貯留タンクへ戻す必要があるため、潤滑ポンプ100は、図3に示すように、吸入孔33側を下に向けて縦置き設置されることが好ましい。
FIG. 5 is a cross-sectional view taken along the line BB in FIG.
In the lubrication pump 100 configured as described above, the outer ring 25 is press-fitted into the bearing hole 73 formed in the housing 71, and a rotation shaft (not shown) is inserted through the inner ring 21. Since the lubricating oil supplied from the lubricating pump 100 needs to be returned to the storage tank by its own weight, the lubricating pump 100 is installed vertically with the suction hole 33 side down as shown in FIG. It is preferable.
軸受孔73の内周面には、複数の吐出孔37に対応する軸方向位置に、溝状の吐出油路75及び吐出油路75を不図示の潤滑部に接続するための接続用油路77が形成される。 On the inner peripheral surface of the bearing hole 73, a groove-like discharge oil passage 75 and a connection oil passage for connecting the discharge oil passage 75 to a lubricating portion (not shown) are disposed at axial positions corresponding to the plurality of discharge holes 37. 77 is formed.
複数の吐出孔37に接続される溝状の吐出油路75は、軸受孔73の内周面の全周に形成して、吐出孔37から吐出される全油量を潤滑部に供給するようにしてもよい。また、図5に示すように、溝状の吐出油路75を、軸受孔73の内周面の一部に形成することで、一部の吐出孔37を塞ぎ、吐出流量を調節して潤滑部に供給することもできる。 Groove-shaped discharge oil passages 75 connected to the plurality of discharge holes 37 are formed in the entire circumference of the inner peripheral surface of the bearing hole 73 so that the total amount of oil discharged from the discharge holes 37 is supplied to the lubricating portion. It may be. Further, as shown in FIG. 5, by forming a groove-like discharge oil passage 75 in a part of the inner peripheral surface of the bearing hole 73, a part of the discharge holes 37 is closed, and the discharge flow rate is adjusted and lubrication is performed. It can also be supplied to the part.
潤滑ポンプ100の全長を軸受孔73に嵌合する場合には、ハウジング71(軸受孔73)の前述した吸入孔33に対応する軸方向位置に、潤滑油供給油路(図示せず)を設ける必要がある。その場合、複数の吸入孔33は、外輪25の外周面に形成された環状の外周側リセス溝35に開口しているので、ハウジング71の潤滑油供給油路と潤滑ポンプ100の吸入孔33との位相を合わせて組み付ける必要がなく、組み付けが容易になる。なお、潤滑ポンプ100は、複数の吸入孔33を含む外輪25の一端部が、ハウジング71から軸方向に突出した状態で軸受孔73に圧入されてもよい。 When the entire length of the lubrication pump 100 is fitted into the bearing hole 73, a lubricating oil supply oil passage (not shown) is provided at an axial position corresponding to the aforementioned suction hole 33 of the housing 71 (bearing hole 73). There is a need. In this case, since the plurality of suction holes 33 are opened in an annular outer recess groove 35 formed on the outer peripheral surface of the outer ring 25, the lubricating oil supply oil passage of the housing 71 and the suction holes 33 of the lubricating pump 100 are provided. As a result, it is not necessary to assemble with the same phase. Note that the lubrication pump 100 may be press-fitted into the bearing hole 73 with one end portion of the outer ring 25 including the plurality of suction holes 33 protruding in the axial direction from the housing 71.
内輪21に嵌合する回転軸は、単列深溝玉軸受である転がり軸受20に滑らかに回転自在に支持される。インペラ51が、回転軸と共に回転すると、インペラ51のポンプ作用によって、潤滑油が潤滑ポンプ100の吸入孔33から吸引される。そして、吸引された潤滑油は、ステータ53の複数の孔57を介して吸込み側ポンプ室55aから吐出側ポンプ室55bへと導かれ、複数の吐出孔37から吐出される。そして、ハウジング71の溝状の吐出油路75、及び接続用油路77を介して摺動部に給油されて潤滑に供される。 The rotating shaft fitted to the inner ring 21 is supported smoothly and freely by the rolling bearing 20 which is a single row deep groove ball bearing. When the impeller 51 rotates together with the rotation shaft, the lubricating oil is sucked from the suction hole 33 of the lubrication pump 100 by the pump action of the impeller 51. The sucked lubricating oil is guided from the suction side pump chamber 55 a to the discharge side pump chamber 55 b through the plurality of holes 57 of the stator 53 and discharged from the plurality of discharge holes 37. Then, the oil is supplied to the sliding portion through the groove-like discharge oil passage 75 and the connection oil passage 77 of the housing 71 for lubrication.
本構成の潤滑ポンプ100は、非容積型ポンプであるので、高速回転域、急加減速時、或いは何らかの障害により油路が閉鎖された場合でも、急激な内部圧力の上昇は起こらず、容積型ポンプと比較して駆動トルクが小さいままであり、原動機の大きな駆動トルクを必要としない。したがって、高速回転軸や急加減速する軸にも適用することができ、高い吐出圧を要しない摺動部を潤滑する用途に好適に使用することができる。 Since the lubrication pump 100 of this configuration is a non-displacement pump, even if the oil passage is closed due to a high-speed rotation region, sudden acceleration / deceleration, or due to some trouble, a sudden increase in internal pressure does not occur. The drive torque remains small compared to the pump and does not require a large drive torque of the prime mover. Therefore, the present invention can also be applied to a high-speed rotating shaft or a shaft that rapidly accelerates or decelerates, and can be suitably used for the purpose of lubricating a sliding portion that does not require high discharge pressure.
図6は、複列深溝玉軸受の転がり軸受20Aの軸方向一端側にポンプ部50が配置された構成例の潤滑ポンプ100Aであり、玉軸受が複列である以外は、上記潤滑ポンプ100と同様であるので、同一部分には、相当符号を付して説明を省略する。 FIG. 6 shows a lubrication pump 100A having a configuration example in which a pump portion 50 is disposed on one end side in the axial direction of a rolling bearing 20A of a double row deep groove ball bearing. Since they are the same, the same parts are denoted by the same reference numerals and the description thereof is omitted.
上記構成の各潤滑ポンプ100,100Aは、例えば、摩擦ローラ式減速機のローラトラクション面等の潤滑に好適に使用できる。 Each of the lubrication pumps 100 and 100A having the above-described configuration can be suitably used for lubricating, for example, a roller traction surface of a friction roller type reduction gear.
本発明は上記の実施形態に限定されるものではなく、実施形態の各構成を相互に組み合わせることや、明細書の記載、並びに周知の技術に基づいて、当業者が変更、応用することも本発明の予定するところであり、保護を求める範囲に含まれる。 The present invention is not limited to the above-described embodiments, and the configurations of the embodiments may be combined with each other, or may be modified or applied by those skilled in the art based on the description of the specification and well-known techniques. The invention is intended and is within the scope of seeking protection.
例えば、転がり軸受は深溝玉軸受に限定されず、アンギュラ玉軸受、4点接触形玉軸受、等の他の形式の軸受であってもよい。また、インペラの羽根部の形状は、斜流形羽根となっているが、これに限定されず、他の形状の羽根部とすることもできる。 For example, the rolling bearing is not limited to a deep groove ball bearing, and may be another type of bearing such as an angular ball bearing, a four-point contact ball bearing, or the like. Moreover, although the shape of the blade | wing part of an impeller is a diagonal flow type blade | wing, it is not limited to this, It can also be set as the blade | wing part of another shape.
以上の通り、本明細書には次の事項が開示されている。
(1) 内輪、外輪、及び前記内輪と前記外輪との間の軸受内部空間における軸方向一端側に、転動自在に複数の転動体が配置された転がり軸受と、
前記軸受内部空間の軸方向他端側に設けられ、前記軸受内部空間に潤滑油を吸引して軸受外部に吐出するポンプ部と、
前記ポンプ部の軸方向両側に設けられ、前記ポンプ部を前記内輪と前記外輪との間に封止する封止部材と、
を備え、
前記ポンプ部は、
前記内輪に外嵌される円環状のインペラベースの外周面に、周方向に亘って複数の羽根部が形成されたインペラと、
前記外輪に内嵌されて前記インペラと協働してポンプ室を構成すると共に、前記ポンプ室を吸込み側と吐出側とに分離するステータと、
を備え、
前記外輪は、前記ポンプ室の前記吸込み側と軸受外部とを接続する複数の吸入孔と、前記ポンプ室の前記吐出側と前記軸受外部とを接続する複数の吐出孔とが形成されていることを特徴とする潤滑ポンプ。
この潤滑ポンプによれば、外部に潤滑ポンプを特別に設けることなく、低駆動トルク、且つ小型の潤滑ポンプにより、高い吐出圧を要しない摺動部に潤滑油を安定して供給することができる。
(2) 前記複数の吸入孔は、前記外輪の外周面に円周方向に沿って形成された外周側リセス溝に開口することを特徴とする上記(1)に記載の潤滑ポンプ。
この潤滑ポンプによれば、潤滑ポンプをハウジングの軸受孔に嵌合させる際に、外周側リセス溝の空間が存在することで、ハウジング側の潤滑油を供給する潤滑油供給油路と、ポンプ本体の吸入孔との位相合わせの必要がなくなる。これにより、潤滑ポンプを簡単、且つ短時間でハウジングに組み付けすることができる。
(3) 前記複数の吐出孔は、前記外輪の内周面に円周方向に沿って形成された内周側リセス溝に開口することを特徴とする上記(1)又は(2)に記載の潤滑ポンプ。
この潤滑ポンプによれば、外輪の内周面に形成された内周側リセス溝が渦巻き型ポンプにおけるケーシングと同様に、効率的に吐出圧力を上昇させることができる。
As described above, the following items are disclosed in this specification.
(1) An inner ring, an outer ring, and a rolling bearing in which a plurality of rolling elements are arranged so as to roll freely on one end side in the axial direction in the bearing inner space between the inner ring and the outer ring,
A pump portion provided on the other axial end side of the bearing internal space, for sucking lubricating oil into the bearing internal space and discharging it to the outside of the bearing;
A sealing member that is provided on both axial sides of the pump portion and seals the pump portion between the inner ring and the outer ring;
With
The pump part is
An impeller having a plurality of blade portions formed on the outer circumferential surface of an annular impeller base fitted to the inner ring over the circumferential direction;
A stator that is fitted into the outer ring and forms a pump chamber in cooperation with the impeller, and separates the pump chamber into a suction side and a discharge side;
With
The outer ring is formed with a plurality of suction holes that connect the suction side of the pump chamber and the outside of the bearing, and a plurality of discharge holes that connect the discharge side of the pump chamber and the outside of the bearing. Lubricating pump characterized by
According to this lubrication pump, the lubricating oil can be stably supplied to the sliding portion that does not require a high discharge pressure by using a small-sized lubrication pump with a low driving torque without specially providing a lubrication pump outside. .
(2) The lubrication pump according to (1), wherein the plurality of suction holes are opened in an outer peripheral recess groove formed in the outer peripheral surface of the outer ring along a circumferential direction.
According to this lubrication pump, when the lubrication pump is fitted into the bearing hole of the housing, there is a space in the outer peripheral recess groove so that the lubricant oil supply passage for supplying the lubricant on the housing side and the pump body There is no need for phasing with the suction hole. Thereby, the lubrication pump can be assembled in the housing in a short time.
(3) In the above (1) or (2), the plurality of discharge holes are opened in an inner circumferential recess groove formed along the circumferential direction on the inner circumferential surface of the outer ring. Lubrication pump.
According to this lubrication pump, the inner peripheral recess groove formed on the inner peripheral surface of the outer ring can efficiently increase the discharge pressure in the same manner as the casing in the spiral pump.
20,20A 転がり軸受
21 内輪
25 外輪
25a 内周面
29 玉(転動体)
33 吸入孔
35 外周側リセス溝
37 吐出孔
39 内周側リセス溝
50 ポンプ部
51 インペラ
51a インペラベース
51b 羽根部
53 ステータ
55 ポンプ室
55a 吸込み側ポンプ室
55b 吐出側ポンプ室
61,62 封止部材
100,100A 潤滑ポンプ
S 軸受内部空間
20, 20A Rolling bearing 21 Inner ring 25 Outer ring 25a Inner peripheral surface 29 Ball (rolling element)
33 suction hole 35 outer peripheral recess groove 37 discharge hole 39 inner peripheral recess groove 50 pump part 51 impeller 51a impeller base 51b blade part 53 stator 55 pump chamber 55a suction side pump chamber 55b discharge side pump chamber 61, 62 sealing member 100 , 100A Lubrication pump S Bearing internal space
Claims (3)
前記軸受内部空間の軸方向他端側に設けられ、潤滑油を前記軸受内部空間と軸受外部との間で吸引及び吐出可能なポンプ部と、
前記ポンプ部の軸方向両側の前記内輪と前記外輪との間に配置された封止部材と、
を備え、
前記ポンプ部は、
前記内輪に外嵌される円環状のインペラベースの外周面に、周方向に亘って複数の羽根部が形成されたインペラと、
前記外輪に内嵌されて前記インペラと協働してポンプ室を構成すると共に、前記ポンプ室を吸込み側と吐出側とに分離するステータと、
を備え、
前記外輪は、前記ポンプ室の前記吸込み側と軸受外部とを接続する複数の吸入孔と、前記ポンプ室の前記吐出側と前記軸受外部とを接続する複数の吐出孔とが形成されていることを特徴とする潤滑ポンプ。 An inner ring, an outer ring, and a rolling bearing in which a plurality of rolling elements are arranged so as to freely roll on one end side in the axial direction in the bearing inner space between the inner ring and the outer ring;
A pump portion provided on the other axial end side of the bearing internal space, and capable of sucking and discharging the lubricating oil between the bearing internal space and the outside of the bearing;
A sealing member disposed between the inner ring and the outer ring on both axial sides of the pump part;
With
The pump part is
An impeller having a plurality of blade portions formed on the outer circumferential surface of an annular impeller base fitted to the inner ring over the circumferential direction;
A stator that is fitted into the outer ring and forms a pump chamber in cooperation with the impeller, and separates the pump chamber into a suction side and a discharge side;
With
The outer ring is formed with a plurality of suction holes that connect the suction side of the pump chamber and the outside of the bearing, and a plurality of discharge holes that connect the discharge side of the pump chamber and the outside of the bearing. Lubricating pump characterized by
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