JPH08284820A - Oscillating plate type compressor - Google Patents
Oscillating plate type compressorInfo
- Publication number
- JPH08284820A JPH08284820A JP7116464A JP11646495A JPH08284820A JP H08284820 A JPH08284820 A JP H08284820A JP 7116464 A JP7116464 A JP 7116464A JP 11646495 A JP11646495 A JP 11646495A JP H08284820 A JPH08284820 A JP H08284820A
- Authority
- JP
- Japan
- Prior art keywords
- lubricating oil
- roller bearing
- thrust
- oscillating plate
- 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.)
- Granted
Links
Classifications
-
- 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
- F04B27/109—Lubrication
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は揺動板式圧縮機に関
し、特にスラストフランジとフロントヘッドの内壁面と
の間に配置されたスラストローラ軸受の耐久性を向上さ
せることができる揺動板式圧縮機に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oscillating plate compressor, and more particularly to an oscillating plate compressor which can improve the durability of a thrust roller bearing arranged between a thrust flange and an inner wall surface of a front head. Regarding
【０００２】[0002]
【従来の技術】従来の揺動板式圧縮機として、図５〜７
に示すものが知られている（実開平６−４３７７号公
報）。2. Description of the Related Art As a conventional rocking plate type compressor, FIGS.
Is known (Japanese Utility Model Publication No. 6-4377).
【０００３】図５は従来の揺動板式圧縮機の縦断面図、
図６は図５の揺動板式圧縮機のフロントヘッドの内壁面
を示す図、図７はフロントヘッドの内壁面のスラストロ
ーラ軸受受面の潤滑油導入溝とスラストローラ軸受のニ
ードルローラとの関係を示す断面図である。FIG. 5 is a vertical sectional view of a conventional rocking plate compressor.
FIG. 6 is a view showing the inner wall surface of the front head of the oscillating plate compressor of FIG. 5, and FIG. 7 is a relationship between the lubricating oil introducing groove of the thrust roller bearing receiving surface of the inner wall surface of the front head and the needle roller of the thrust roller bearing. FIG.
【０００４】この揺動板式圧縮機は、シャフト１０５に
固定され、且つスラストローラ軸受１３３（例えばニー
ドルローラ軸受）を介してフロントヘッド１０４の内壁
面のスラストローラ軸受受面１３７に回転可能に支持さ
れたスラストフランジ１４０と、スラストフランジ１４
０に連結され、シャフト１０５と一体に回転するドライ
ブハブ１４１と、ドライブハブ１４１に揺動可能に装着
された揺動板１１０と、フロントヘッド１０４のボス部
１０４ａの内周面とシャフト１０５のフロント側端部の
外周面との隙間をシールするシール部材１５５が収容さ
れたシール室１６９と、フロントヘッド１０４内の潤滑
油をシール室１６９へ供給する潤滑油供給路２００とを
備えている。This oscillating plate compressor is fixed to a shaft 105 and is rotatably supported on a thrust roller bearing receiving surface 137 on the inner wall surface of the front head 104 via a thrust roller bearing 133 (for example, a needle roller bearing). Thrust flange 140 and thrust flange 14
Drive hub 141 which is connected to 0 and rotates integrally with the shaft 105, the swing plate 110 swingably mounted on the drive hub 141, the inner peripheral surface of the boss portion 104a of the front head 104 and the front surface of the shaft 105. A seal chamber 169 accommodating a seal member 155 that seals a gap between the outer peripheral surface of the side end portion and a lubricating oil supply path 200 that supplies the lubricating oil in the front head 104 to the seal chamber 169 is provided.
【０００５】前記スラストローラ軸受１３３には、異音
発生防止のために予圧（プレロード）とピストン１０７
の圧縮反力とが加わる。The thrust roller bearing 133 has a preload (preload) and a piston 107 for preventing abnormal noise.
And the compression reaction force of.
【０００６】前記潤滑油供給路２００は、フロントヘッ
ド１０４の内壁面のスラストローラ軸受受面１３７に設
けられた潤滑油導入溝１５１，１５２と、潤滑油導入溝
１５１，１５２を通じて導入された潤滑油をシール室１
６９に供給する潤滑油供給孔１５３，１５４とで構成さ
れている。The lubricating oil supply passage 200 has lubricating oil introduction grooves 151 and 152 provided on the thrust roller bearing receiving surface 137 on the inner wall surface of the front head 104, and lubricating oil introduced through the lubricating oil introduction grooves 151 and 152. Seal room 1
It is composed of lubricating oil supply holes 153 and 154 which are supplied to the unit 69.
【０００７】フロントヘッド１０４内でオイル分離され
た潤滑油は、潤滑油導入溝１５１，１５２から潤滑油供
給孔１５３，１５４を経てシール室１６９内に送り込ま
れるとともに、シャフト１０５のフロント側端部を回転
可能に支持するラジアル軸受１２６が収容された軸受収
容室１６８にも送り込まれる。シール部材１５５とシャ
フト１０５、ラジアル軸受１２６とシャフト１０５、等
の摺動部は、送り込まれた潤滑油によって潤滑と冷却と
が行われる。シール室１６９及び軸受収容室１６８の潤
滑油はフロントヘッド１０４内に排出される。The lubricating oil separated in the front head 104 is fed from the lubricating oil introducing grooves 151, 152 into the sealing chamber 169 through the lubricating oil supply holes 153, 154, and at the front end of the shaft 105. It is also fed into the bearing accommodating chamber 168 in which the radial bearing 126 that rotatably supports is accommodated. The sliding parts such as the seal member 155 and the shaft 105 and the radial bearing 126 and the shaft 105 are lubricated and cooled by the lubricating oil fed. The lubricating oil in the seal chamber 169 and the bearing housing chamber 168 is discharged into the front head 104.
【０００８】[0008]
【発明が解決しようとする課題】ところが、スラストロ
ーラ軸受１３３のレース１３５は薄いため、スラストフ
ランジ１４０が回転し、スラストローラ軸受１３３のニ
ードルローラ１３４がレース１３５上を回転移動して、
図７に示すように、レース１３５を介してニードルロー
ラ１３４が潤滑油導入溝１５１，１５２とスラスト方向
で対向したとき（ニードルローラ１３４と潤滑油導入溝
１５１，１５２とが平行になったとき）、図７に示すよ
うに、潤滑油導入溝１５１，１５２と対向するレース１
３５の一部分が潤滑油導入溝１５１，１５２内へ陥没す
るように変形し、その凹んだ部分の両端１３５ａ，１３
５ｂが摩耗して焼付きを起こし、スラストローラ軸受１
３３の寿命を縮めるという問題があった。However, since the race 135 of the thrust roller bearing 133 is thin, the thrust flange 140 rotates and the needle roller 134 of the thrust roller bearing 133 rotationally moves on the race 135.
As shown in FIG. 7, when the needle roller 134 faces the lubricating oil introducing grooves 151, 152 through the race 135 in the thrust direction (when the needle roller 134 and the lubricating oil introducing grooves 151, 152 are parallel to each other). As shown in FIG. 7, the race 1 facing the lubricating oil introducing grooves 151, 152
Part of 35 is deformed so as to be depressed into the lubricating oil introducing grooves 151, 152, and both ends 135a, 13 of the recessed parts are deformed.
5b wears and causes seizure, and thrust roller bearing 1
There was a problem of shortening the life of 33.
【０００９】この発明はこのような事情に鑑みてなされ
たもので、その課題はスラストローラ軸受のレースの変
形による摩耗、焼付きを防ぎ、スラストローラ軸受の耐
久性を向上させることができる揺動板式圧縮機を提供す
ることである。The present invention has been made in view of the above circumstances, and its object is to prevent the abrasion and seizure due to the deformation of the race of the thrust roller bearing, and to improve the durability of the thrust roller bearing. It is to provide a plate compressor.
【００１０】[0010]
【課題を解決するための手段】前述の課題を解決するた
め請求項１記載の発明の揺動板式圧縮機は、回転軸に設
けられ、且つスラストローラ軸受を介してハウジングの
内壁面に回転可能に支持された駆動力伝達部材と、前記
駆動力伝達部材に揺動可能に装着され、前記駆動力伝達
部材の回転に連れて揺動する揺動板と、前記ハウジング
の内壁面のスラストローラ軸受受面に設けられ、前記ハ
ウジング内部の潤滑油を導く潤滑油導入溝と、前記潤滑
油導入溝を通じて導入された潤滑油を、前記ハウジング
と前記回転軸との摺動部へ供給する潤滑油供給孔とを備
えた揺動板式圧縮機において、前記潤滑油導入溝は前記
スラストローラ軸受のローラの回転中心軸に対し非平行
である。In order to solve the above-mentioned problems, the oscillating plate compressor according to the invention of claim 1 is provided on a rotary shaft and is rotatable on the inner wall surface of the housing via a thrust roller bearing. A drive force transmitting member supported by the drive force transmitting member, a swing plate mounted on the drive force transmitting member so as to swing, and swinging as the drive force transmitting member rotates, and a thrust roller bearing on the inner wall surface of the housing. A lubricating oil introduction groove that is provided on the receiving surface and guides lubricating oil inside the housing, and a lubricating oil supply that supplies the lubricating oil introduced through the lubricating oil introduction groove to the sliding portion between the housing and the rotary shaft. In the oscillating plate compressor having a hole, the lubricating oil introducing groove is not parallel to the rotation center axis of the roller of the thrust roller bearing.
【００１１】請求項２記載の発明の揺動板式圧縮機は、
前記潤滑油導入溝の始端部が、前記潤滑油供給孔と連通
する前記潤滑油導入溝の終端部よりも前記回転軸の回転
方向の前側に位置している。The oscillating plate compressor according to the second aspect of the invention is
A starting end portion of the lubricating oil introduction groove is located on a front side in a rotation direction of the rotary shaft with respect to an end portion of the lubricating oil introduction groove communicating with the lubricating oil supply hole.
【００１２】請求項３記載の発明の揺動板式圧縮機は、
少なくとも２つの前記潤滑油導入溝のうち、一方の潤滑
油導入溝の始端部が前記潤滑油供給孔と連通する前記潤
滑油導入溝の終端部よりも前記回転軸の回転方向の前側
に位置し、他方の潤滑油導入溝の始端部が前記潤滑油供
給孔と連通する前記潤滑油導入溝の終端部よりも前記回
転軸の回転方向の後側に位置している。The oscillating plate compressor according to the third aspect of the invention is
Of at least two of the lubricating oil introducing grooves, a starting end of one lubricating oil introducing groove is located on a front side in a rotation direction of the rotary shaft with respect to an end of the lubricating oil introducing groove communicating with the lubricating oil supply hole. The starting end portion of the other lubricating oil introducing groove is located on the rear side in the rotation direction of the rotary shaft with respect to the ending portion of the lubricating oil introducing groove communicating with the lubricating oil supply hole.
【００１３】[0013]
【作用】請求項１記載の発明の揺動板式圧縮機では、潤
滑油導入溝をスラストローラ軸受のローラの回転中心軸
に対し非平行にしたので、潤滑油導入溝はスラストロー
ラ軸受のローラとクロスし、スラストローラ軸受のレー
スの一部がローラによって潤滑油導入溝内に陥没（変
形）しない。In the oscillating plate compressor according to the first aspect of the present invention, the lubricating oil introducing groove is not parallel to the center axis of rotation of the roller of the thrust roller bearing. Because of the crossing, a part of the race of the thrust roller bearing is not depressed (deformed) in the lubricating oil introduction groove by the roller.
【００１４】請求項２記載の発明の揺動板式圧縮機で
は、潤滑油導入溝の始端部を、潤滑油供給孔と連通する
潤滑油導入溝の終端部よりも回転軸の回転方向の前側に
配置したので、潤滑油導入溝をスラストローラ軸受のロ
ーラの回転中心軸に対し平行にしたときに較べ、潤滑油
が潤滑油導入溝に入りや易くなる。In the oscillating plate compressor according to the second aspect of the present invention, the starting end portion of the lubricating oil introducing groove is located forward of the ending portion of the lubricating oil introducing groove communicating with the lubricating oil supply hole in the rotating direction of the rotary shaft. Because of the arrangement, the lubricating oil is more likely to enter the lubricating oil introducing groove than when the lubricating oil introducing groove is parallel to the rotation center axis of the roller of the thrust roller bearing.
【００１５】請求項３記載の発明の揺動板式圧縮機で
は、少なくとも２つの潤滑油導入溝のうち、一方の潤滑
油導入溝の始端部を潤滑油供給孔と連通する潤滑油導入
溝の終端部よりも回転軸の回転方向の前側に配置し、他
方の潤滑油導入溝の始端部を潤滑油供給孔と連通する潤
滑油導入溝の終端部よりも回転軸の回転方向の後側に配
置したので、一方の潤滑油導入溝を通じて摺動部に入り
込んだ潤滑油は、他方の潤滑油供給孔を通じてハウジン
グ内部に排出される。In the oscillating plate compressor according to the third aspect of the present invention, of the at least two lubricating oil introducing grooves, the starting end of one lubricating oil introducing groove communicates with the lubricating oil supply hole to terminate the lubricating oil introducing groove. Is located on the front side in the rotating direction of the rotating shaft, and the starting end of the other lubricating oil introducing groove is located on the rear side in the rotating direction of the rotating shaft than the end of the lubricating oil introducing groove communicating with the lubricating oil supply hole. Therefore, the lubricating oil that has entered the sliding portion through the one lubricating oil introduction groove is discharged into the housing through the other lubricating oil supply hole.
【００１６】[0016]
【実施例】以下この発明の実施例を図面に基づいて説明
する。Embodiments of the present invention will be described below with reference to the drawings.
【００１７】図１はこの発明の第１実施例に係る揺動板
式圧縮機の要部を示す拡大断面図、図２は図１の揺動板
式圧縮機の全体を示す縦断面図、図３は図２の揺動板式
圧縮機のフロントヘッドの端面図である。FIG. 1 is an enlarged cross-sectional view showing an essential part of an oscillating plate type compressor according to a first embodiment of the present invention, FIG. 2 is a vertical sectional view showing the whole oscillating plate type compressor of FIG. 1, and FIG. FIG. 3 is an end view of the front head of the oscillating plate compressor of FIG. 2.
【００１８】この揺動板式圧縮機のシリンダブロック１
の一端面にはバルブプレート２を介してリヤヘッド３
が、他端面にはフロントヘッド（ハウジング）４がそれ
ぞれ固定されている。シリンダブロック１には、シャフ
ト（回転軸）５を中心にして周方向に所定間隔おきに複
数のシリンダボア６が配設されている。これらのシリン
ダボア６内にはそれぞれピストン７が摺動自在に収容さ
れている。Cylinder block 1 of this oscillating plate compressor
The rear head 3 is attached to one end face of the rear plate 3 through the valve plate 2.
However, front heads (housings) 4 are fixed to the other end surfaces, respectively. In the cylinder block 1, a plurality of cylinder bores 6 are arranged at predetermined intervals in the circumferential direction around a shaft (rotational axis) 5. A piston 7 is slidably accommodated in each of the cylinder bores 6.
【００１９】前記フロントヘッド４内にはクランク室
（ハウジング内部）８が形成され、このクランク室８内
には、シャフト５の回転に連動してヒンジボール９を中
心に揺動する揺動板１０が収容されている。この揺動板
１０はコネクチングロッド１１を介してピストン７に連
結され、揺動板１０の揺動によりピストン７がシリンダ
ボア６内を往復運動する。この揺動板１０の傾斜角度は
クランク室８の圧力に応じて変化する。フロントヘッド
４のボス部４ａの内周面とシャフト５のフロント側端部
の外周面との間にはシール室６９が形成され、シール室
６９内にはシール部材（摺動部）５５が収容されてい
る。A crank chamber (inside the housing) 8 is formed in the front head 4, and a swing plate 10 that swings around a hinge ball 9 in conjunction with the rotation of the shaft 5 is formed in the crank chamber 8. Is housed. The rocking plate 10 is connected to the piston 7 via a connecting rod 11, and the rocking of the rocking plate 10 causes the piston 7 to reciprocate in the cylinder bore 6. The tilt angle of the swing plate 10 changes according to the pressure in the crank chamber 8. A seal chamber 69 is formed between the inner peripheral surface of the boss portion 4a of the front head 4 and the outer peripheral surface of the front end of the shaft 5, and a seal member (sliding portion) 55 is accommodated in the seal chamber 69. Has been done.
【００２０】前記リヤヘッド３内には、吐出室１２と、
この吐出室１２の周囲に位置する吸入室１３とが形成さ
れている。吐出室１２内は隔壁１４によって吐出空間１
２ａと吐出空間１２ｂとに仕切られ、両吐出空間１２
ａ，１２ｂは、隔壁１４に穿設された絞り孔１４ａを介
して連通している。In the rear head 3, a discharge chamber 12 and
A suction chamber 13 located around the discharge chamber 12 is formed. The inside of the discharge chamber 12 is divided by the partition wall 14 into the discharge space 1
2a and the discharge space 12b are divided into two discharge spaces 12
The a and 12b communicate with each other through a throttle hole 14a formed in the partition wall 14.
【００２１】前記バルブプレート２には、シリンダボア
６と吐出空間１２ａとを連通させる吐出ポート１６と、
シリンダボア６と吸入室１３とを連通させる吸入ポート
１５とが、それぞれ周方向に所定間隔おきに設けられて
いる。吐出ポート１６は吐出弁１７により開閉され、吐
出弁１７はバルブプレート２のリヤヘッド側端面に弁押
さえ１８とともにボルト１９により固定され、ボルト１
９はバルブプレート２の中心孔２ａを介してシリンダブ
ロック１のねじ孔２０に螺着されている。また、吸入ポ
ート１５は吸入弁２１により開閉され、吸入弁２１はバ
ルブプレート２とシリンダブロック１との間に配設され
ている。ボルト１９には、吐出空間１２ａの高圧の冷媒
ガスをシリンダブロック１の小径孔２２へ導く図示しな
いガイド孔が設けられている。The valve plate 2 has a discharge port 16 for communicating the cylinder bore 6 with the discharge space 12a,
Suction ports 15 that connect the cylinder bore 6 and the suction chamber 13 are provided at predetermined intervals in the circumferential direction. The discharge port 16 is opened / closed by a discharge valve 17, and the discharge valve 17 is fixed to the end face of the valve plate 2 on the rear head side by a bolt 19 together with a valve retainer 18.
9 is screwed into the screw hole 20 of the cylinder block 1 through the center hole 2a of the valve plate 2. The suction port 15 is opened and closed by a suction valve 21, and the suction valve 21 is arranged between the valve plate 2 and the cylinder block 1. The bolt 19 is provided with a guide hole (not shown) for guiding the high-pressure refrigerant gas in the discharge space 12a to the small diameter hole 22 of the cylinder block 1.
【００２２】前記シリンダブロック１の中央部には、互
いに連通するねじ孔２０、小径孔２２及び大径孔２３が
シリンダブロック１の中心線に沿って設けられている。
小径孔２２にはラジアル軸受２４が、大径孔２３にはス
ラスト軸受２５がそれぞれ収容されている。ラジアル軸
受２４及びスラスト軸受２５はシャフト５のリヤ側端部
を支持し、シャフト５のフロント側端部はフロントヘッ
ド４の軸受収容室６８に収容されたラジアル軸受（摺動
部）２６によって回転可能に支持されている。A screw hole 20, a small diameter hole 22 and a large diameter hole 23, which communicate with each other, are provided in the center of the cylinder block 1 along the center line of the cylinder block 1.
A radial bearing 24 is accommodated in the small diameter hole 22, and a thrust bearing 25 is accommodated in the large diameter hole 23. The radial bearing 24 and the thrust bearing 25 support the rear end of the shaft 5, and the front end of the shaft 5 is rotatable by a radial bearing (sliding part) 26 housed in a bearing housing chamber 68 of the front head 4. Supported by.
【００２３】また、シリンダブロック１には吸入室１３
とクランク室８とを連通させる連通路３１が設けられ、
この連通路３１の途中には圧力調整弁３２が設けられ、
この圧力調整弁３２により吸入室１３内とクランク室８
内との圧力調整が行われる。The cylinder block 1 has a suction chamber 13
And a communication passage 31 that connects the crank chamber 8 with the crank chamber 8,
A pressure adjusting valve 32 is provided in the middle of the communication passage 31,
By means of this pressure adjusting valve 32, the inside of the suction chamber 13 and the crank chamber 8
Pressure adjustment with the inside is performed.
【００２４】前記シャフト５のフロント側端部にはシャ
フト５の回転をドライブハブ４１に伝達するためのスラ
ストフランジ４０が固定され、このスラストフランジ４
０はスラストローラ軸受（例えばニードルローラ軸受）
３３を介してフロントヘッド４の内壁面のスラストロー
ラ軸受受面３７に回転可能に押し当てられている。スラ
ストフランジ４０の一端部とドライブハブ４１の一端部
とはリンクアーム４２を介して連結され、スラストフラ
ンジ４０の他端部に対しドライブハブ４１の他端部が離
れたり、接触したりすることができる。スラストフラン
ジ４０とドライブハブ４１とで駆動力伝達部材が構成さ
れる。A thrust flange 40 for transmitting the rotation of the shaft 5 to a drive hub 41 is fixed to an end portion of the shaft 5 on the front side.
0 is a thrust roller bearing (eg needle roller bearing)
It is rotatably pressed against the thrust roller bearing receiving surface 37 on the inner wall surface of the front head 4 via 33. One end of the thrust flange 40 and one end of the drive hub 41 are connected via a link arm 42, and the other end of the drive hub 41 can be separated from or in contact with the other end of the thrust flange 40. it can. The thrust flange 40 and the drive hub 41 constitute a driving force transmission member.
【００２５】前記スラストローラ軸受３３は、図１に示
すように、ニードルローラ（ローラ）３４と、このニー
ドルローラ３４を挟む環状のレース３５，３６とから構
成されている。レース３５は、フロントヘッド４の取付
段部３８に嵌着され、スラストローラ軸受受面３７に当
接している。レース３６は、スラストフランジ４０の取
付凹部３９に嵌合されている。レース３５は、半径方向
へ突出する突片３５ａを有している。また、スラスト軸
受３３には異音発生防止のために予圧（プレロード）が
加えられている。As shown in FIG. 1, the thrust roller bearing 33 is composed of a needle roller (roller) 34 and annular races 35 and 36 sandwiching the needle roller 34. The race 35 is fitted on the mounting step portion 38 of the front head 4 and is in contact with the thrust roller bearing receiving surface 37. The race 36 is fitted in the mounting recess 39 of the thrust flange 40. The race 35 has a projecting piece 35a that projects in the radial direction. A preload is applied to the thrust bearing 33 to prevent abnormal noise.
【００２６】フロントヘッド４の内壁面下部には、図３
に示すように、レース３５の突片３５ａを両側から挟持
する一対のリブ４８ａが一体成形されている。また、フ
ロントヘッド４の内壁面上部には一対のオイル分離用の
凹部４９，５０が設けられ、凹部４９，５０と連通する
潤滑油導入溝５１，５２がスラストローラ軸受受面３７
に設けられている。潤滑油導入溝５１，５２は、フロン
トヘッド４に設けられた潤滑油供給路５３，５４にそれ
ぞれ連通している。In the lower part of the inner wall surface of the front head 4, FIG.
As shown in, a pair of ribs 48a that sandwich the projecting piece 35a of the race 35 from both sides are integrally formed. Further, a pair of recesses 49, 50 for oil separation are provided in the upper portion of the inner wall surface of the front head 4, and lubricating oil introduction grooves 51, 52 communicating with the recesses 49, 50 are provided in the thrust roller bearing receiving surface 37.
It is provided in. The lubricating oil introducing grooves 51 and 52 communicate with the lubricating oil supply passages 53 and 54 provided in the front head 4, respectively.
【００２７】潤滑油導入溝５１，５２は図３に示すよう
にスラストローラ軸受３３のニードルローラ３４の回転
中心軸に対して傾いている。すなわち、潤滑油導入溝５
１，５２とニードルローラ３４の回転中心軸とは非平行
であり、潤滑油導入溝５１，５２とニードルローラ３４
の回転中心軸とはクロスしている。As shown in FIG. 3, the lubricating oil introducing grooves 51 and 52 are inclined with respect to the center axis of rotation of the needle roller 34 of the thrust roller bearing 33. That is, the lubricating oil introduction groove 5
1, 52 and the center axis of rotation of the needle roller 34 are not parallel to each other, and the lubricating oil introducing grooves 51, 52 and the needle roller 34
It intersects with the rotation center axis of.
【００２８】前記揺動板１０は、ラジアル軸受６０及び
スラスト軸受６１，６２を介してドライブハブ４１に揺
動可能に装着されている。ドライブハブ４１は、シャフ
ト５に軸線方向に摺動可能に装着されたヒンジボール９
を介して、シャフト５に装着されている。ドライブハブ
４１の回転と傾斜動作とが妨げられないように、ドライ
ブハブ４１のヒンジボール受面４１ｂはヒンジボール９
の外周面に遊嵌されている。ドライブハブ４１のボス部
４１ａの先端部外周面には雄ネジ６３が設けられ、ボス
部４１ａの外周にはバランスウエイト６４及びロックワ
ッシャ６５が装着され、バランスウエイト６４及びロッ
クワッシャ６５はボス部４１ａの雄ネジ６３に締め込ま
れるロックナット６６によって固定される。The swing plate 10 is swingably attached to the drive hub 41 via a radial bearing 60 and thrust bearings 61 and 62. The drive hub 41 includes a hinge ball 9 mounted on the shaft 5 slidably in the axial direction.
It is attached to the shaft 5 via. The hinge ball receiving surface 41b of the drive hub 41 is fixed to the hinge ball 9 so that the rotation and the tilting operation of the drive hub 41 are not hindered.
Is loosely fitted to the outer peripheral surface of the. A male screw 63 is provided on the outer peripheral surface of the boss portion 41a of the drive hub 41, and a balance weight 64 and a lock washer 65 are attached to the outer periphery of the boss portion 41a. The balance weight 64 and the lock washer 65 are mounted on the boss portion 41a. It is fixed by a lock nut 66 which is screwed into the male screw 63 of.
【００２９】ヒンジボール９とスラストフランジ４０と
の間のシャフト５の外周には、巻バネ４４が装着され、
この巻バネ４４によりヒンジボール９がシリンダブロッ
ク１側へ付勢されている。また、シャフト５にはストッ
パ４５が固定され、ストッパ４５とヒンジボール９との
間のシャフト５の外周には、複数の皿バネ４６及び巻バ
ネ４７が順次装着され、これらのバネ４６，４７により
ヒンジボール９がスラストフランジ４０側へ付勢されて
いる。A coil spring 44 is mounted on the outer circumference of the shaft 5 between the hinge ball 9 and the thrust flange 40.
The hinge ball 9 is biased toward the cylinder block 1 by the coil spring 44. A stopper 45 is fixed to the shaft 5, and a plurality of disc springs 46 and a winding spring 47 are sequentially mounted on the outer periphery of the shaft 5 between the stopper 45 and the hinge ball 9. The hinge ball 9 is biased toward the thrust flange 40 side.
【００３０】揺動板１０には半径方向にレストレイント
ピン７０が挿入され、レストレイントピン７０の一端部
にはスリッパ６７が装着されている。A restraint pin 70 is inserted in the swing plate 10 in the radial direction, and a slipper 67 is attached to one end of the restraint pin 70.
【００３１】次に、この揺動板式圧縮機の作動を説明す
る。Next, the operation of this oscillating plate compressor will be described.
【００３２】図示しない車載エンジンの回転動力がシャ
フト５に伝達されると、シャフト５はスラストフランジ
４０及びドライブハブ４１とともに回転し、その回転に
ともなって揺動板１０が揺動し、この揺動によりピスト
ン７がシリンダボア６内を往復動し、その結果シリンダ
ボア６内の容積が変化し、この容積変化によって冷媒ガ
スの吸入、圧縮及び吐出が順次行なわれ、揺動板１０の
傾斜角度に応じた容量の高圧冷媒ガスが吐出される。When the rotational power of the vehicle-mounted engine (not shown) is transmitted to the shaft 5, the shaft 5 rotates together with the thrust flange 40 and the drive hub 41, and the rocking plate 10 rocks with the rotation, and this rocking. As a result, the piston 7 reciprocates in the cylinder bore 6, and as a result the volume in the cylinder bore 6 changes, and due to this volume change, refrigerant gas is sucked in, compressed and discharged in sequence, and in accordance with the tilt angle of the oscillating plate 10. A volume of high pressure refrigerant gas is discharged.
【００３３】すなわち、熱負荷が小さくなり圧力調整弁
３２が連通路３１を閉じ、クランク室８内の圧力が増加
すると揺動板１０の傾斜角度が小さくなり、これによっ
てピストン７のストローク量が少なくなって吐出容量が
減少する。That is, when the heat load is reduced and the pressure regulating valve 32 closes the communication passage 31 and the pressure in the crank chamber 8 is increased, the inclination angle of the oscillating plate 10 is reduced, which reduces the stroke amount of the piston 7. Therefore, the discharge capacity is reduced.
【００３４】また、冷媒ガス中には潤滑油が含まれてい
るので、ラジアル軸受２４，２６，６０やスラスト軸受
等２５，３３，６１，６２の潤滑が行われるが、低負荷
時や高速運転時などの最小吐出量状態では、冷媒ガスの
流量が減少するので潤滑油の供給量も減る。Further, since the refrigerant gas contains lubricating oil, the radial bearings 24, 26, 60 and the thrust bearings 25, 33, 61, 62 are lubricated, but at the time of low load or high speed operation. In the minimum discharge amount state such as time, the flow rate of the refrigerant gas decreases, so the supply amount of lubricating oil also decreases.
【００３５】熱負荷が大きくなり圧力調整弁３２が連通
路３１を開き、クランク室８内の圧力が減少すると揺動
板１０の傾斜角度が大きくなり、これによってピストン
７のストローク量が増えて吐出容量が多くなる。When the heat load increases and the pressure regulating valve 32 opens the communication passage 31 and the pressure in the crank chamber 8 decreases, the tilt angle of the oscillating plate 10 increases, which increases the stroke amount of the piston 7 and discharges it. Increased capacity.
【００３６】圧縮機の運転によってスラストローラ軸受
３３にピストン７の圧縮反力が加わるため、スラストロ
ーラ軸受３３には圧縮反力と前述した予圧との合力に相
当するスラスト方向の荷重が加わることになるが、潤滑
油導入溝５１，５２は図３に示すようにスラストローラ
軸受３３のニードルローラ３４の回転中心軸に対して傾
いているので、潤滑油導入溝５１，５２とスラストロー
ラ軸受３３のニードルローラ３４とはクロスし、スラス
ト軸受３３のレース３５の一部がニードルローラ３４に
よって潤滑油導入溝５１，５２内に陥没しない。Since the compression reaction force of the piston 7 is applied to the thrust roller bearing 33 by the operation of the compressor, a load in the thrust direction corresponding to the resultant force of the compression reaction force and the above-mentioned preload is applied to the thrust roller bearing 33. However, since the lubricating oil introducing grooves 51, 52 are inclined with respect to the rotation center axis of the needle roller 34 of the thrust roller bearing 33 as shown in FIG. 3, the lubricating oil introducing grooves 51, 52 and the thrust roller bearing 33 are Since the needle roller 34 crosses the needle roller 34, a part of the race 35 of the thrust bearing 33 is not depressed by the needle roller 34 into the lubricating oil introducing grooves 51, 52.
【００３７】また、クランク室８内の冷媒ガスはフロン
トヘッド４の凹部４９，５０でオイル分離され、その潤
滑油はレース受面３７の潤滑油導入溝５１，５２を経由
して潤滑油供給路５３，５４を通り、シール部５５内へ
供給され、潤滑油の一部は潤滑油供給路５３，５４の途
中に設けられた開口５３ａ，５４ａからラジアル軸受２
６に供給される。したがって、シール部５５のシール性
が補完されるとともにラジアル軸受２６の潤滑及びスラ
スト軸受３３の冷却が行なわれる。The refrigerant gas in the crank chamber 8 is oil-separated by the recesses 49, 50 of the front head 4, and the lubricating oil is passed through the lubricating oil introducing grooves 51, 52 of the race receiving surface 37 to supply the lubricating oil. A part of the lubricating oil supplied to the seal portion 55 through 53, 54 is provided through the openings 53a, 54a provided in the lubricating oil supply passages 53, 54, to the radial bearing 2.
6. Therefore, the sealing performance of the seal portion 55 is complemented, and the radial bearing 26 is lubricated and the thrust bearing 33 is cooled.
【００３８】この第１実施例の揺動板式圧縮機によれ
ば、潤滑油導入溝５１，５２とスラストローラ軸受３３
のニードルローラ３４とはクロスするので、スラスト軸
受３３のレース３５の一部がニードルローラ３４によっ
て潤滑油導入溝５１，５２内に陥没（変形）せず、潤滑
油導入溝５１，５２と対向するレース３５の一部分の摩
耗、焼付きを防ぐことができ、スラスト軸受３３の耐久
性を向上させることができる。According to the oscillating plate type compressor of the first embodiment, the lubricating oil introducing grooves 51 and 52 and the thrust roller bearing 33 are provided.
Since the needle roller 34 crosses the needle roller 34, a part of the race 35 of the thrust bearing 33 does not sink (deform) into the lubricating oil introducing grooves 51, 52 by the needle roller 34 and faces the lubricating oil introducing grooves 51, 52. It is possible to prevent wear and seizure of a part of the race 35, and improve the durability of the thrust bearing 33.
【００３９】図４はこの発明の他の実施例に係る揺動板
式圧縮機のフロントヘッドの内壁面を示す図であって、
同図（ａ）は第２実施例に係る揺動板式圧縮機のフロン
トヘッドの内壁面を示す図、同図（ｂ）は第３実施例に
係る揺動板式圧縮機のフロントヘッドの内壁面を示す
図、同図（ｃ）は第４実施例に係る揺動板式圧縮機のフ
ロントヘッドの内壁面を示す図である。前述の第１実施
例と共通する部分には同一符号を付して説明を省略す
る。FIG. 4 is a view showing the inner wall surface of the front head of the oscillating plate type compressor according to another embodiment of the present invention.
FIG. 7A is a diagram showing the inner wall surface of the front head of the oscillating plate compressor according to the second embodiment, and FIG. 7B is the inner wall surface of the front head of the oscillating plate compressor according to the third embodiment. FIG. 11C is a diagram showing the inner wall surface of the front head of the oscillating plate compressor according to the fourth embodiment. The same parts as those of the first embodiment described above are designated by the same reference numerals and the description thereof will be omitted.
【００４０】前述の第１実施例では、潤滑油導入溝５
１，５２をスラストローラ軸受３３のニードルローラ３
４の回転中心軸に対して傾けて、潤滑油導入溝５１，５
２とスラストローラ軸受３３のニードルローラ３４とを
クロスさせた場合について述べたが、第２実施例では、
図４（ａ）に示すように、潤滑油導入溝７１，７２をそ
れぞれ曲線状に形成し、潤滑油導入溝７１，７２の始端
部７１ａ，７２ａを、潤滑油供給孔５３，５４と連通す
る潤滑油導入溝７１，７２の終端部７１ｂ，７２ｂより
もシャフト５の回転方向の前側に配置した。In the first embodiment described above, the lubricating oil introducing groove 5 is used.
1, 52 to the needle roller 3 of the thrust roller bearing 33
Inclining with respect to the rotation center axis of 4, the lubricating oil introducing grooves 51, 5
2 and the needle roller 34 of the thrust roller bearing 33 are crossed with each other, but in the second embodiment,
As shown in FIG. 4A, the lubricating oil introducing grooves 71, 72 are formed in a curved shape, and the starting end portions 71a, 72a of the lubricating oil introducing grooves 71, 72 are communicated with the lubricating oil supply holes 53, 54. The lubricating oil introduction grooves 71, 72 are arranged on the front side in the rotation direction of the shaft 5 with respect to the end portions 71b, 72b.
【００４１】この第２実施例によれば、潤滑油導入溝７
１，７２の始端部の向きがスラストローラ軸受受面３７
の外周縁によって形成される仮想円の接線方向に近付く
ので、シャフト５が回転したとき、潤滑油が潤滑油導入
溝７１，７２に入り易くなり、シール室６８及び軸受収
容室６９の潤滑と冷却とが促進される。According to the second embodiment, the lubricating oil introducing groove 7
The direction of the starting end portions of 1, 72 is the thrust roller bearing receiving surface 37.
Since it approaches the tangential direction of the virtual circle formed by the outer peripheral edge of the, the lubricating oil easily enters the lubricating oil introduction grooves 71 and 72 when the shaft 5 rotates, and the seal chamber 68 and the bearing accommodating chamber 69 are lubricated and cooled. And are promoted.
【００４２】第３実施例では、図４（ｂ）に示すよう
に、潤滑油導入溝８１，８２のほぼ中間部をスラストロ
ーラ軸受３３のニードルローラ３４の回転中心軸に対し
て所定角度傾斜させた。In the third embodiment, as shown in FIG. 4 (b), approximately the middle portion of the lubricating oil introducing grooves 81, 82 is inclined at a predetermined angle with respect to the central axis of rotation of the needle roller 34 of the thrust roller bearing 33. It was
【００４３】このようにしても第１の実施例と同様の作
用効果を得ることができる。Even in this case, the same operational effect as that of the first embodiment can be obtained.
【００４４】第４実施例では、図４（ｃ）に示すよう
に、潤滑油導入溝９１，９２をスラストローラ軸受３３
の半径方向に対して所定角度傾斜させ、一方の潤滑油導
入溝９１の始端部９１ａを、潤滑油供給孔５３と連通す
る潤滑油導入溝９１の終端部９１ｂよりもシャフト５の
回転方向の前側に配置し、他方の潤滑油導入溝９２の始
端部９２ａを、潤滑油供給孔５４と連通する潤滑油導入
溝９２の終端部９２ｂよりもシャフト５の回転方向の後
側に配置した。すなわち、シャフト５の回転方向に対し
て、一方の潤滑油導入溝９１の傾斜方向を潤滑油が潤滑
油導入溝９１内に入り込む方向に、他方の潤滑油導入溝
９２の傾斜方向を潤滑油が潤滑油導入溝９２から排出さ
れる方向にした。In the fourth embodiment, as shown in FIG. 4 (c), the lubricating oil introducing grooves 91 and 92 are formed in the thrust roller bearing 33.
At a predetermined angle with respect to the radial direction, the start end 91a of one of the lubricating oil introducing grooves 91 communicates with the lubricating oil supply hole 53, and the front side in the rotational direction of the shaft 5 with respect to the terminating end 91b of the lubricating oil introducing groove 91. The starting end portion 92a of the other lubricating oil introducing groove 92 is arranged rearward of the ending portion 92b of the lubricating oil introducing groove 92 communicating with the lubricating oil supply hole 54 in the rotational direction of the shaft 5. That is, with respect to the rotation direction of the shaft 5, one of the lubricating oil introducing grooves 91 is inclined in the direction in which the lubricating oil enters the lubricating oil introducing groove 91, and the other lubricating oil introducing groove 92 is inclined in the inclined direction. The lubricant was introduced from the lubricating oil introducing groove 92.
【００４５】この第４実施例によれば、潤滑油導入溝９
１、潤滑油供給孔５３からシール室６８及び軸受収容室
６９に入り込んだ潤滑油は潤滑油供給孔５４、潤滑油導
入溝９２を通じてクランク室８に排出されるので、潤滑
油によるシール室６８及び軸受収容室６９の冷却効果が
向上する。According to the fourth embodiment, the lubricating oil introducing groove 9
1. The lubricating oil that has entered the seal chamber 68 and the bearing accommodating chamber 69 from the lubricating oil supply hole 53 is discharged to the crank chamber 8 through the lubricating oil supply hole 54 and the lubricating oil introduction groove 92. The cooling effect of the bearing housing 69 is improved.
【００４６】なお、前述の各実施例では２つの潤滑油導
入溝を設けた場合について述べたが、潤滑油導入溝の数
は１つでも、３つ以上でもよい。In each of the above-mentioned embodiments, the case where two lubricating oil introducing grooves are provided has been described, but the number of lubricating oil introducing grooves may be one or three or more.
【００４７】[0047]
【発明の効果】以上説明したように請求項１記載の発明
の揺動板式圧縮機によれば、潤滑油導入溝はスラストロ
ーラ軸受のローラとクロスし、スラストローラ軸受のレ
ースの一部がローラによって潤滑油導入溝内に陥没（変
形）しないので、潤滑油導入溝と対向するレースの一部
分の摩耗、焼付きを防ぐことができ、スラストローラ軸
受の耐久性を向上させることができる。As described above, according to the oscillating plate compressor of the first aspect of the invention, the lubricating oil introduction groove intersects the roller of the thrust roller bearing, and a part of the race of the thrust roller bearing is the roller. Since it does not sink (deform) in the lubricating oil introducing groove, it is possible to prevent abrasion and seizure of a part of the race facing the lubricating oil introducing groove, and it is possible to improve the durability of the thrust roller bearing.
【００４８】請求項２記載の発明の揺動板式圧縮機によ
れば、潤滑油が潤滑油導入溝に入りや易くなり、摺動部
の潤滑と冷却とが促進される。According to the oscillating plate compressor of the second aspect of the invention, the lubricating oil easily enters the lubricating oil introduction groove, and the lubrication and cooling of the sliding portion are promoted.
【００４９】請求項３記載の発明の揺動板式圧縮機によ
れば、一方の潤滑油導入溝を通じて摺動部に入り込んだ
潤滑油は、他方の潤滑油供給孔を通じてハウジング内部
に排出されるので、潤滑油による摺動部の冷却効果が向
上する。According to the oscillating plate compressor of the third aspect of the invention, the lubricating oil that has entered the sliding portion through one lubricating oil introduction groove is discharged into the housing through the other lubricating oil supply hole. Further, the cooling effect of the sliding portion by the lubricating oil is improved.
【図１】図１はこの発明の第１実施例に係る揺動板式圧
縮機の要部を示す拡大断面図である。FIG. 1 is an enlarged sectional view showing a main part of an oscillating plate compressor according to a first embodiment of the present invention.
【図２】図２は図１の揺動板式圧縮機の全体を示す縦断
面図である。FIG. 2 is a vertical cross-sectional view showing the entire oscillating plate compressor shown in FIG.
【図３】図３は図２の揺動板式圧縮機のフロントヘッド
の端面図である。FIG. 3 is an end view of a front head of the oscillating plate compressor shown in FIG.
【図４】図４はこの発明の他の実施例に係る揺動板式圧
縮機のフロントヘッドの端面図である。FIG. 4 is an end view of a front head of an oscillating plate compressor according to another embodiment of the present invention.
【図５】図５は従来の揺動板式圧縮機の縦断面図であ
る。FIG. 5 is a vertical cross-sectional view of a conventional rocking plate compressor.
【図６】図６は図５の揺動板式圧縮機のフロントヘッド
の内壁面を示す図である。6 is a diagram showing an inner wall surface of a front head of the oscillating plate compressor shown in FIG.
【図７】図７はフロントヘッドの内壁面のレース受面の
潤滑油導入溝とニードルローラスラスト軸受のニードル
ローラとの関係を示す断面図である。FIG. 7 is a cross-sectional view showing the relationship between the lubricating oil introduction groove on the race receiving surface of the inner wall surface of the front head and the needle roller of the needle roller thrust bearing.
４ フロントヘッド ５ シャフト １０ 揺動板 ３３ スラストローラ軸受 ３７ スラストローラ軸受受面 ４０ スラストフランジ ４１ ドライブハブ ５１，５２，７１，７２，８１，８２，９１，９２ 潤
滑油導入溝 ５３，５４ 潤滑油供給孔4 Front Head 5 Shaft 10 Swing Plate 33 Thrust Roller Bearing 37 Thrust Roller Bearing Receiving Surface 40 Thrust Flange 41 Drive Hub 51, 52, 71, 72, 81, 82, 91, 92 Lubricating Oil Introductory 53, 54 Lubricating Oil Supply Hole
フロントページの続き (72)発明者 石田 欣之 埼玉県大里郡江南町大字千代字東原39番地 株式会社ゼクセル江南工場内Front Page Continuation (72) Inventor Kinno Ishida 39, Toyo-ji, Chiyo-ji, Konan-cho, Osato-gun, Saitama Prefecture Zexel Konan Factory
Claims (3)
軸受を介してハウジングの内壁面に回転可能に支持され
た駆動力伝達部材と、 前記駆動力伝達部材に揺動可能に装着され、前記駆動力
伝達部材の回転に連れて揺動する揺動板と、 前記ハウジングの内壁面のスラストローラ軸受受面に設
けられ、前記ハウジング内部の潤滑油を導く潤滑油導入
溝と、 前記潤滑油導入溝を通じて導入された潤滑油を、前記ハ
ウジングと前記回転軸との摺動部へ供給する潤滑油供給
孔とを備えた揺動板式圧縮機において、 前記潤滑油導入溝は前記スラストローラ軸受のローラの
回転中心軸に対し非平行であることを特徴とする揺動板
式圧縮機。1. A drive force transmitting member provided on a rotary shaft and rotatably supported on an inner wall surface of a housing via a thrust roller bearing; and a drive force transmitting member swingably attached to the drive force transmitting member. A swing plate that swings with the rotation of the force transmission member, a lubricating oil introduction groove that is provided on a thrust roller bearing receiving surface of the inner wall surface of the housing, and guides lubricating oil inside the housing, and the lubricating oil introduction groove In a oscillating plate compressor having a lubricating oil supply hole for supplying the lubricating oil introduced through the housing to the sliding portion of the rotary shaft, the lubricating oil introduction groove is formed in the roller of the thrust roller bearing. An oscillating plate compressor characterized by being non-parallel to the central axis of rotation.
油供給孔と連通する前記潤滑油導入溝の終端部よりも前
記回転軸の回転方向の前側に位置していることを特徴と
する請求項１記載の揺動板式圧縮機。2. A starting end portion of the lubricating oil introducing groove is located on a front side in a rotation direction of the rotary shaft with respect to an ending portion of the lubricating oil introducing groove communicating with the lubricating oil supply hole. The oscillating plate compressor according to claim 1.
ち、一方の潤滑油導入溝の始端部が前記潤滑油供給孔と
連通する前記潤滑油導入溝の終端部よりも前記回転軸の
回転方向の前側に位置し、他方の潤滑油導入溝の始端部
が前記潤滑油供給孔と連通する前記潤滑油導入溝の終端
部よりも前記回転軸の回転方向の後側に位置しているこ
とを特徴とする請求項１記載の揺動板式圧縮機。3. The rotation direction of the rotating shaft is greater than the end portion of the lubricating oil introduction groove where the starting end portion of one lubricating oil introduction groove of the at least two lubricating oil introduction grooves communicates with the lubricating oil supply hole. Is located on the front side, and the starting end portion of the other lubricating oil introducing groove is located on the rear side in the rotation direction of the rotating shaft with respect to the ending portion of the lubricating oil introducing groove communicating with the lubricating oil supply hole. The oscillating plate compressor according to claim 1.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11646495A JP3567346B2 (en) | 1995-04-18 | 1995-04-18 | Compressor |
| DE1996114384 DE19614384C2 (en) | 1995-04-18 | 1996-04-11 | Swash plate compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11646495A JP3567346B2 (en) | 1995-04-18 | 1995-04-18 | Compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH08284820A true JPH08284820A (en) | 1996-10-29 |
| JP3567346B2 JP3567346B2 (en) | 2004-09-22 |
Family
ID=14687763
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP11646495A Expired - Lifetime JP3567346B2 (en) | 1995-04-18 | 1995-04-18 | Compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP3567346B2 (en) |
| DE (1) | DE19614384C2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106715905A (en) * | 2014-09-24 | 2017-05-24 | 法雷奥日本株式会社 | Compressor |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5937735A (en) * | 1996-12-12 | 1999-08-17 | Sanden Corporation | Swash-plate compressor having a thrust race with a radial flange insuring supply of a lubricating oil to a drive shaft bearing |
| DE50009171D1 (en) | 1999-08-06 | 2005-02-10 | Luk Fahrzeug Hydraulik | CO 2 - COMPRESSOR |
| DE102015217448A1 (en) * | 2015-09-11 | 2017-03-16 | Magna Powertrain Bad Homburg GmbH | Compressor with thrust bearing |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH061782U (en) * | 1992-06-08 | 1994-01-14 | 株式会社豊田自動織機製作所 | Variable capacity swash plate compressor |
-
1995
- 1995-04-18 JP JP11646495A patent/JP3567346B2/en not_active Expired - Lifetime
-
1996
- 1996-04-11 DE DE1996114384 patent/DE19614384C2/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106715905A (en) * | 2014-09-24 | 2017-05-24 | 法雷奥日本株式会社 | Compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3567346B2 (en) | 2004-09-22 |
| DE19614384A1 (en) | 1996-10-24 |
| DE19614384C2 (en) | 1998-07-09 |
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