JP3604458B2 - Thrust roller bearing for swash plate compressor - Google Patents

Thrust roller bearing for swash plate compressor Download PDF

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Publication number
JP3604458B2
JP3604458B2 JP16738995A JP16738995A JP3604458B2 JP 3604458 B2 JP3604458 B2 JP 3604458B2 JP 16738995 A JP16738995 A JP 16738995A JP 16738995 A JP16738995 A JP 16738995A JP 3604458 B2 JP3604458 B2 JP 3604458B2
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Japan
Prior art keywords
swash plate
race
roller bearing
thrust roller
crowning
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Expired - Fee Related
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JP16738995A
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Japanese (ja)
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JPH0914131A (en
Inventor
賢二 高橋
紘造 橋本
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Koyo Seiko Co Ltd
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Koyo Seiko Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • F04B27/1063—Actuating-element bearing means or driving-axis bearing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/30—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for axial load mainly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/088—Ball or roller bearings self-adjusting by means of crowning
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/50—Crowning, e.g. crowning height or crowning radius

Description

【０００１】
【発明の属する技術分野】
本発明は、回転軸に固着される斜板の回転動作によってピストンをシリンダ内で軸方向に往復動作させる斜板式圧縮機の前記斜板と非回転のシリンダとの間に設けられるスラストころ軸受に関する。
【０００２】
【従来の技術】
従来の斜板式圧縮機として、例えば実願昭６１−１７１４０６号（実開昭６３−７８１７７号公報）のマイクロフィルムや実願平２−１２７３６号（実開平３−１０４５２５号公報）のマイクロフィルムなどに示すようなものがある。
【０００３】
一般的に、斜板式圧縮機の斜板を支持するスラストころ軸受の支持形態としては、斜板の受け座に対して一方レースの外面の外径側を、また、シリンダの受け座に対して他方レースの外面の内径側を、それぞれ部分的に当接させる片当たり支持形態が採用されている。
【０００４】
そして、スラストころ軸受に取付誤差やピストンの荷重変動に伴う振動発生を抑制する目的から、一方レースの外径側を他方レース側へ、また、他方レースの内径側を一方レース側へそれぞれ所要量押圧する状態に設定することにより、スラストころ軸受に対して所要のアキシャル荷重からなる予圧を与えている。このような組み付け状態では、スラストころ軸受の内径が軸方向一方側に、外径側が軸方向他方側にと、若干ではあるが偏り、円錐形にたわんでいる。
【０００５】
【発明が解決しようとする課題】
ところで、上記従来例のスラストころ軸受では、次のような問題がある。
【０００６】
つまり、斜板式圧縮機では、そのピストンの動きに伴いスラストころ軸受に対して作用するアキシャル方向の負荷が増減変動するために、スラストころ軸受の両レースのたわみ量が時事刻々と変動することになる。しかも、このたわみ量は、一方レースの外径側と他方レースの内径側とで若干の差を生じることが分かっている。このために、ころとレースとの局部に対する過大負荷によるエッジロードが発生しやすくなるなど、軸受機能や寿命の低下につながる。
【０００７】
これに対して、ころにクラウニングを施すことが考えられている。このクラウニングにも、従来から、ころの全長にわたって連続的に形成するフルクラウニングと、ころの両端にのみ部分的に形成する部分クラウニングとがある。
【０００８】
しかしながら、前者は、最大たわみ時の局部負荷を無くす場合に有効であるものの、たわみ量が減少すると接触面圧が高くなるために短寿命となりやすくなる。一方の後者は、常用のたわみ時に長寿命とする場合に有効であるものの、最大たわみ時にころ端部への負荷が過大になるために短寿命となりやすくなる。
【０００９】
したがって、本発明の目的は、斜板式圧縮機用のスラストころ軸受において、レースのたわみの変動にかかわらず、軸受機能の安定化と寿命の向上を図ることである。
【００１０】
【課題を解決するための手段】
本発明は、回転軸に固着される斜板の回転動作によってピストンをシリンダ内で軸方向に往復動作させる斜板式圧縮機の前記斜板と非回転のシリンダとの間に設けられるスラストころ軸受において、次のように構成した。
【００１１】
本発明では、前記斜板の受け座に対して、外面の内径側または外径側のいずれか一方が部分的に当接される第１レースと、非回転のシリンダの受け座に対して、外面の外径側または内径側のいずれか一方が部分的に当接される第２レースと、両レースに挟まれる複数のころとを備え、かつ、ころの長手方向中間部分には、レースのたわみが小さいときに接触面圧を小さくする曲率の小さな第１のクラウニングが形成されていて、ころの長手方向両端部分には、斜板回転に伴うレースのたわみ時の湾曲形状に近似する放物線に沿う第２のクラウニングが形成されている。
【００１２】
【発明の実施の形態】
以下、本発明の詳細を図１ないし図５に示す実施例に基づいて説明する。
【００１３】
図１ないし図５は本発明の一実施例にかかり、図１は、斜板式圧縮機の縦断面図、図２は、斜板式圧縮機の斜板の支持部の縦断面図、図３は、斜板支持用のスラストころ軸受に備えるころのクラウニングの説明図、図４は、スラストころ軸受の組み付け状態を示す上半分の縦断面図、図５は、スラストころ軸受のアキシャル荷重とレースたわみ量との関係を示すグラフである。
【００１４】
図例の斜板式圧縮機１において、２，３は二つのシリンダ、４，５はシリンダヘッド、６は二つのシリンダ２，３の間に跨がって配されるピストン、７は駆動用の回転軸、８は回転軸７に外嵌固定されかつ外周がボール９およびシュー１０を介してピストン６に係合される斜板、１１は回転軸支持用のラジアルころ軸受、１２は斜板支持用のスラストころ軸受、１３はサイドカバーである。
【００１５】
前述の二つのシリンダ２，３の内径側の円筒部のそれぞれ斜板８寄りの端面において内周側には、スラストころ軸受１２の受け座としての環状凸部１４，１５が形成されている。
【００１６】
また、斜板８のボス部１６の両端面において外周側には、スラストころ軸受１２の受け座としての環状凸部１７，１８が形成されている。
【００１７】
スラストころ軸受１２は、軸方向に対向配置される第１、第２のレース１９，２０と、両レース１９，２０の間に保持器２１で保持される複数のころ２２とを備えている。これら両レース１９，２０およびころ２２は、軸受鋼などの高炭素鋼系材料に浸炭窒化または窒化などの処理を施して、表面部の基質を内部より高炭素・高窒素とするとともに、表面部に炭・窒化物を形成させ、焼入れを行うことにより、耐摩耗性を向上して長寿命化を図っている。
【００１８】
さらに、ころ２２の外周面には、それぞれ、クラウニングが施されている。具体的に、図３に示すように、ころ２２の長手方向中間部分Ｅ１には、両レース１９，２０のたわみが小さいときに接触面圧を小さくする曲率の小さな第１のクラウニング２３が形成されていて、ころ２２の長手方向両端部分Ｅ２，Ｅ２には、斜板８の回転に伴う両レース１９，２０のたわみ時の湾曲形状に近似する放物線（Ｙ＝ａＸ２、ａは定数）に沿う第２のクラウニング２４が形成されている。なお、第１のクラウニング２３の最小径部位から最大径部位までの膨出寸法ｄは、１μｍ以下に設定するのが好ましい。そして、第１のクラウニング２３と第２のクラウニング２４との継ぎ目についても、滑らかな曲線となっている。
【００１９】
このスラストころ軸受１２の第１レース１９の外面（斜板８のボス部１６の端面に対向する面）において外径側は、ボス部１６の環状凸部１７，１８に対して部分的に当接させられており、一方、第２レース２０の外面（シリンダ２，３の端面に対向する面）において内径側は、シリンダ２，３の環状凸部１４，１５に対して部分的に当接させられている。そして、第１レース１９の外径側を第２レース２０側（矢印Ａ側）へ、また、第２レース２０の内径側を第１レース１９側（矢印Ｂ側）へ、それぞれ所要量押圧する状態に組み付けることにより、所要のアキシャル荷重からなる予圧を与えている。この組み付け状態では、図４に示すように、スラストころ軸受１２がほぼ円錐形に弾性的にたわんでいる。図では、たわみを誇張して表している。
【００２０】
ところで、前述のたわみは、図５のグラフに示すように、第１レース１９の外径側と第２レース２０の内径側とで若干の差を生じる。また、ピストン６によるアキシャル方向の負荷の変動でもって両レース１９，２０のたわみ量が増減変動することになる。これらの現象は、避けられない。しかしながら、本実施例の場合では、ころ２２に両レース１９，２０のたわみを考慮した特殊なクラウニング２３，２４を施しているので、たわみ量が比較的小さいときには、ころ２２の長手方向中間部分Ｅ１と両レース１９，２０との接触面圧を低く保つことができ、軸受性能の安定化を達成できるようになる。一方、たわみ量が最大のときには、ころ２２の端部にかかる負荷を軽減してエッジロードの発生を阻止することができ、寿命向上を達成できるようになる。
【００２１】
このように、両レース１９，２０のたわみ量が変動しても、その変動に応じて、ころ２２と両レース１９，２０との局部に対する過大負荷の発生を抑制できるようになる。そして、ころ２２および両レース１９，２０を前述したように耐摩耗性を向上させているから、前述したクラウニング２３，２４の作用、効果とあいまって、軸受機能の安定化と長寿命化を達成できるようになる。
【００２２】
【発明の効果】
本発明では、要するに、ころの全長にクラウニングを形成するのであるが、このクラウニングとして、ころの長手方向中間部分と両端部分とで異なる曲率の曲線からなる二種の特殊なものを組み合わせた構成としている。
【００２３】
したがって、本発明のスラストころ軸受では、斜板式圧縮機からの影響によってレースのたわみ量が変動しても、その変動に応じて、ころとレースとの局部に対する過大負荷の発生を抑制できるようになり、軸受機能の安定化と寿命の向上を図ることができる。
【図面の簡単な説明】
【図１】本発明の一実施例のスラストころ軸受を備える斜板式圧縮機の縦断面図
【図２】図１の斜板式圧縮機の斜板の支持部の縦断面図
【図３】斜板支持用のスラストころ軸受に備えるころのクラウニングの説明図
【図４】スラストころ軸受の取付形態を示す上半分の縦断面図
【図５】スラストころ軸受のアキシャル荷重とレースたわみ量との関係を示すグラフ
【符号の説明】
１ 斜板式圧縮機
２，３ シリンダ
７ 回転軸
８ 斜板
１２ スラストころ軸受
１４，１５ シリンダの環状凸部
１７，１８ 斜板の環状凸部
１９ 第１レース
２０ 第２レース
２２ ころ
２３ 第１のクラウニング
２４ 第２のクラウニング[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a thrust roller bearing provided between a swash plate and a non-rotating cylinder of a swash plate compressor in which a piston reciprocates in a cylinder in an axial direction by a rotation operation of a swash plate fixed to a rotating shaft. .
[0002]
[Prior art]
Conventional swash plate type compressors include, for example, a microfilm disclosed in Japanese Utility Model Application No. 61-171406 (Japanese Utility Model Application Laid-Open No. 63-78177) and a microfilm disclosed in Japanese Utility Model Application No. 2-12736 (Japanese Utility Model Application No. 3-104525). There is something like that shown in
[0003]
Generally, as a support form of a thrust roller bearing for supporting a swash plate of a swash plate type compressor, the outer diameter side of the outer surface of one race with respect to a bearing seat of a swash plate and a bearing shape of a cylinder with respect to a bearing seat of a cylinder. On the other hand, a one-sided support mode is adopted in which the inner diameter side of the outer surface of the race is partially brought into contact with each other.
[0004]
Then, in order to suppress the generation of vibrations due to the mounting error and the load fluctuation of the piston in the thrust roller bearing, the outer diameter side of one race is set to the other race side, and the inner diameter side of the other race is set to the one race side. By setting the pressing state, a preload consisting of a required axial load is applied to the thrust roller bearing. In such an assembled state, the inner diameter of the thrust roller bearing is slightly biased and conically bent to one side in the axial direction and the outer diameter side to the other side in the axial direction.
[0005]
[Problems to be solved by the invention]
By the way, the above-mentioned conventional thrust roller bearing has the following problems.
[0006]
In other words, in the swash plate type compressor, the axial load acting on the thrust roller bearing fluctuates with the movement of the piston, so that the amount of deflection of both races of the thrust roller bearing fluctuates every moment. Become. In addition, it is known that the amount of deflection causes a slight difference between the outer diameter side of one race and the inner diameter side of the other race. For this reason, an edge load due to an excessive load on the local portions of the rollers and the race is likely to occur, leading to a reduction in the bearing function and life.
[0007]
On the other hand, crowning the rollers has been considered. Conventionally, the crowning includes a full crowning formed continuously over the entire length of the roller and a partial crowning formed only at both ends of the roller.
[0008]
However, although the former is effective in eliminating the local load at the time of the maximum deflection, when the amount of deflection is reduced, the contact surface pressure is increased, so that the life tends to be short. On the other hand, the latter is effective when the life is extended at the time of ordinary bending, but the load on the roller end becomes excessive at the time of the maximum bending, so that the life tends to be short.
[0009]
Accordingly, it is an object of the present invention to stabilize the bearing function and improve the life of a thrust roller bearing for a swash plate type compressor regardless of the fluctuation of the race deflection.
[0010]
[Means for Solving the Problems]
The present invention relates to a thrust roller bearing provided between the swash plate and a non-rotating cylinder of a swash plate type compressor in which a piston reciprocates in a cylinder in an axial direction by rotating a swash plate fixed to a rotating shaft. The configuration was as follows.
[0011]
In the present invention, with respect to the receiving seat of the swash plate, the first race in which one of the inner surface and the outer surface of the outer surface is partially abutted, and the receiving seat of the non-rotating cylinder, A second race in which one of the outer surface and the inner surface of the outer surface is partially abutted, and a plurality of rollers sandwiched between the two races, and a longitudinal intermediate portion of the rollers includes A first crowning having a small curvature for reducing the contact surface pressure when the deflection is small is formed. At both ends in the longitudinal direction of the rollers, a parabola approximating a curved shape at the time of the deflection of the race due to the rotation of the swash plate is provided. A second crowning along is formed.
[0012]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, the present invention will be described in detail with reference to the embodiments shown in FIGS.
[0013]
1 to 5 relate to an embodiment of the present invention. FIG. 1 is a longitudinal sectional view of a swash plate compressor, FIG. 2 is a longitudinal sectional view of a swash plate support portion of the swash plate compressor, and FIG. FIG. 4 is an explanatory view of crowning of a roller provided in a thrust roller bearing for supporting a swash plate, FIG. 4 is a longitudinal sectional view of an upper half showing an assembled state of the thrust roller bearing, and FIG. 5 is an axial load and race deflection of the thrust roller bearing. It is a graph which shows the relationship with quantity.
[0014]
In the swash plate type compressor 1 shown in the figure, reference numerals 2 and 3 denote two cylinders, reference numerals 4 and 5 denote cylinder heads, reference numeral 6 denotes a piston disposed between the two cylinders 2 and 3, and reference numeral 7 denotes a drive. The rotating shaft 8 is a swash plate which is fitted and fixed on the rotating shaft 7 and whose outer periphery is engaged with the piston 6 via the ball 9 and the shoe 10, 11 is a radial roller bearing for supporting the rotating shaft, and 12 is a swash plate support. Thrust roller bearing, 13 is a side cover.
[0015]
Annular convex portions 14 and 15 as receiving seats of the thrust roller bearing 12 are formed on the inner peripheral side of the end surfaces of the cylindrical portions on the inner diameter side of the two cylinders 2 and 3 near the swash plate 8, respectively.
[0016]
Further, annular convex portions 17 and 18 as receiving seats of the thrust roller bearing 12 are formed on the outer peripheral sides of both end surfaces of the boss portion 16 of the swash plate 8.
[0017]
The thrust roller bearing 12 includes first and second races 19 and 20 that are arranged to face each other in the axial direction, and a plurality of rollers 22 that are held by a cage 21 between the races 19 and 20. The races 19 and 20 and the rollers 22 are formed by subjecting a high-carbon steel-based material such as a bearing steel to a treatment such as carbonitriding or nitriding, so that the substrate on the surface is made higher in carbon and nitrogen than inside, and Carbon and nitride are formed and quenched to improve wear resistance and extend the life.
[0018]
Further, the outer peripheral surfaces of the rollers 22 are respectively crowned. Specifically, as shown in FIG. 3, a first crowning 23 having a small curvature is formed in a longitudinally intermediate portion E1 of the roller 22 to reduce the contact surface pressure when the deflection of the races 19 and 20 is small. In addition, both ends E2 and E2 in the longitudinal direction of the roller 22 follow a parabola (Y = aX 2 , where a is a constant) that approximates the curved shape when the two races 19 and 20 bend with the rotation of the swash plate 8. A second crowning 24 is formed. In addition, it is preferable that the swelling dimension d of the first crowning 23 from the minimum diameter portion to the maximum diameter portion is set to 1 μm or less. The seam between the first crowning 23 and the second crowning 24 also has a smooth curve.
[0019]
On the outer surface of the first race 19 of the thrust roller bearing 12 (the surface facing the end surface of the boss portion 16 of the swash plate 8), the outer diameter side partially touches the annular convex portions 17 and 18 of the boss portion 16. On the other hand, the inner diameter side of the outer surface of the second race 20 (the surface facing the end surfaces of the cylinders 2 and 3) partially abuts the annular projections 14 and 15 of the cylinders 2 and 3. Have been allowed. The outer diameter side of the first race 19 is pressed toward the second race 20 (arrow A side), and the inner diameter side of the second race 20 is pressed against the first race 19 side (arrow B side). By assembling in the state, a preload consisting of a required axial load is given. In this assembled state, as shown in FIG. 4, the thrust roller bearing 12 is elastically bent in a substantially conical shape. In the figure, the deflection is exaggerated.
[0020]
By the way, the above-described deflection causes a slight difference between the outer diameter side of the first race 19 and the inner diameter side of the second race 20, as shown in the graph of FIG. In addition, the amount of deflection of both races 19 and 20 increases and decreases due to a change in the axial load caused by the piston 6. These phenomena are inevitable. However, in the case of the present embodiment, since the rollers 22 are provided with the special crownings 23 and 24 in consideration of the deflection of the races 19 and 20, when the amount of deflection is relatively small, the longitudinal intermediate portion E1 of the rollers 22 is provided. And the contact surface pressure between the two races 19 and 20 can be kept low, and the bearing performance can be stabilized. On the other hand, when the deflection amount is the maximum, the load applied to the end portion of the roller 22 can be reduced to prevent the edge load from occurring, and the life can be improved.
[0021]
In this way, even if the amount of deflection of the two races 19 and 20 fluctuates, the occurrence of an excessive load on the roller 22 and the local portions of the two races 19 and 20 can be suppressed in accordance with the fluctuation. Since the wear resistance of the rollers 22 and the races 19 and 20 is improved as described above, the stabilization of the bearing function and the prolongation of the service life are achieved in combination with the operation and effect of the crowning 23 and 24 described above. become able to.
[0022]
【The invention's effect】
In the present invention, in short, crowning is formed on the entire length of the roller, and as this crowning, a configuration combining two special types of curved lines having different curvatures at the longitudinal middle portion and both end portions of the roller is used. I have.
[0023]
Therefore, in the thrust roller bearing of the present invention, even if the deflection amount of the race fluctuates due to the influence of the swash plate type compressor, it is possible to suppress the occurrence of an excessive load on the roller and the race locally according to the fluctuation. Therefore, it is possible to stabilize the bearing function and improve the life.
[Brief description of the drawings]
1 is a longitudinal sectional view of a swash plate type compressor having a thrust roller bearing according to an embodiment of the present invention; FIG. 2 is a longitudinal sectional view of a swash plate supporting portion of the swash plate type compressor of FIG. 1; Explanatory drawing of roller crowning provided in a thrust roller bearing for supporting a plate. [Fig. 4] Longitudinal cross-sectional view of the upper half showing the mounting form of the thrust roller bearing. [Fig. 5] Relationship between axial load of thrust roller bearing and race deflection. [Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Swash plate type compressor 2, 3 Cylinder 7 Rotary shaft 8 Swash plate 12 Thrust roller bearing 14, 15 Cylinder convex portion 17, 18 Circular plate convex portion 19 First race 20 Second race 22 Roller 23 First Crowning 24 Second Crowning

Claims (1)

回転軸に固着される斜板の回転動作によってピストンをシリンダ内で軸方向に往復動作させる斜板式圧縮機の前記斜板と非回転のシリンダとの間に設けられるスラストころ軸受であって、
前記斜板の受け座に対して、外面の内径側または外径側のいずれか一方が部分的に当接される第１レースと、
非回転のシリンダの受け座に対して、外面の外径側または内径側のいずれか一方が部分的に当接される第２レースと、
両レースに挟まれる複数のころとを備え、
かつ、ころの長手方向中間部分には、レースのたわみが小さいときに接触面圧を小さくする曲率の小さな第１のクラウニングが形成されていて、ころの長手方向両端部分には、斜板回転に伴うレースのたわみ時の湾曲形状に近似する放物線に沿う第２のクラウニングが形成されている、ことを特徴とする斜板式圧縮機用のスラストころ軸受。A thrust roller bearing provided between the swash plate and a non-rotating cylinder of a swash plate compressor in which a piston reciprocates in a cylinder axially by a rotating operation of a swash plate fixed to a rotating shaft,
A first race in which one of the inner diameter side and the outer diameter side of the outer surface is partially in contact with the receiving seat of the swash plate;
A second race in which either the outer surface or the inner surface of the outer surface is partially in contact with a receiving seat of the non-rotating cylinder;
With multiple rollers sandwiched between both races,
In addition, a first crowning with a small curvature is formed at a longitudinal middle portion of the roller to reduce the contact surface pressure when the deflection of the race is small, and at both longitudinal ends of the roller, a swash plate is rotated. A thrust roller bearing for a swash plate type compressor, wherein a second crowning is formed along a parabola approximating a curved shape at the time of the accompanying deflection of the race.
JP16738995A 1995-07-03 1995-07-03 Thrust roller bearing for swash plate compressor Expired - Fee Related JP3604458B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP16738995A JP3604458B2 (en) 1995-07-03 1995-07-03 Thrust roller bearing for swash plate compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP16738995A JP3604458B2 (en) 1995-07-03 1995-07-03 Thrust roller bearing for swash plate compressor

Publications (2)

Publication Number Publication Date
JPH0914131A JPH0914131A (en) 1997-01-14
JP3604458B2 true JP3604458B2 (en) 2004-12-22

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Application Number Title Priority Date Filing Date
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Country Status (1)

Country Link
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007142001A1 (en) 2006-06-08 2007-12-13 Ntn Corporation Roller and thrust roller bearing

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3886350B2 (en) * 2001-08-30 2007-02-28 Ｎｔｎ株式会社 Swash plate compressor
EP1298334A3 (en) 2001-09-26 2005-11-16 Ntn Corporation Roller thrust bearing
JP2003156050A (en) * 2001-11-22 2003-05-30 Ntn Corp Thrust needle bearing
JP3871537B2 (en) * 2001-09-26 2007-01-24 Ｎｔｎ株式会社 Thrust roller bearing
DE102013213332A1 (en) * 2013-07-08 2015-01-08 Schaeffler Technologies Gmbh & Co. Kg Support bearing, in particular roller

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007142001A1 (en) 2006-06-08 2007-12-13 Ntn Corporation Roller and thrust roller bearing

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