JPH08270553A - Swash plate type compressor - Google Patents
Swash plate type compressorInfo
- Publication number
- JPH08270553A JPH08270553A JP7077721A JP7772195A JPH08270553A JP H08270553 A JPH08270553 A JP H08270553A JP 7077721 A JP7077721 A JP 7077721A JP 7772195 A JP7772195 A JP 7772195A JP H08270553 A JPH08270553 A JP H08270553A
- Authority
- JP
- Japan
- Prior art keywords
- oil
- chamber
- swash plate
- hole
- bearings
- 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
Landscapes
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Compressor (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、高圧冷媒ガスの油分離
機構を内蔵した斜板式圧縮機の改良に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a swash plate compressor having an oil separation mechanism for high pressure refrigerant gas.
【０００２】[0002]
【従来の技術】主として車両空調用に供される斜板式圧
縮機では、可動部分の潤滑に供される潤滑油が冷媒ガス
中にミスト状に混在されている。したがって、圧縮機か
ら吐出される冷媒ガスと共に混在油粒がそのまま冷凍回
路に吐出循環されると、この油粒が蒸発器の内壁等に付
着して熱交換の効率を低下させる。2. Description of the Related Art In a swash plate type compressor mainly used for air conditioning of a vehicle, lubricating oil used for lubricating a movable portion is mixed in a refrigerant gas in a mist form. Therefore, if the mixed oil particles are discharged and circulated as they are in the refrigeration circuit together with the refrigerant gas discharged from the compressor, the oil particles adhere to the inner wall of the evaporator and the like, and the efficiency of heat exchange is reduced.
【０００３】このため、従来では、圧縮機から凝縮器に
至る高圧管路中に油分離器を別設して、分離された潤滑
油を還油配管を介して圧縮機内へ戻すように構成したも
のが実用されているが、機器、配管の増設に伴う総合的
な冷凍回路構成の幅輳化に加えて、小径、かつ長尺状に
形成された還油配管に目詰りなどの事故も生じ易いの
で、近時、圧縮機に直接油分離機構を内蔵させた構成の
ものも提案されている。Therefore, conventionally, an oil separator is separately provided in the high-pressure pipe line from the compressor to the condenser, and the separated lubricating oil is returned to the compressor through the return oil pipe. However, in addition to making the total refrigeration circuit configuration wider due to the expansion of equipment and piping, accidents such as clogging of the return oil piping formed with a small diameter and long shape also occurred. Since it is easy, it has recently been proposed that the compressor directly incorporates an oil separation mechanism.
【０００４】[0004]
【発明が解決しようとする課題】さて、上述した油分離
機構内蔵型の圧縮機では、機内の高圧領域で分離された
分離油を回収する油溜室と、該分離油を還給する低圧領
域（例えば斜板室）とが還油孔によって連通せしめられ
ているが、適正な還油量の保持や、機台停止後の貯溜油
枯渇時、該還油孔を経由して生じる高圧冷媒ガスの逆流
抑制といった点を考慮して浮子弁など各種の弁装置が配
設されているが、還油孔の通路断面積が小さいだけに作
動不良を生じやすいといった問題がある。In the above-described compressor having a built-in oil separation mechanism, the oil reservoir chamber for collecting the separated oil separated in the high pressure area in the machine and the low pressure area for returning the separated oil. (For example, the swash plate chamber) communicates with the return oil hole. However, when the proper amount of return oil is maintained and the stored oil is exhausted after the machine is stopped, the high pressure refrigerant gas generated via the return oil hole Various valve devices such as a float valve are provided in consideration of the backflow suppression, but there is a problem that malfunction is likely to occur because the passage cross-sectional area of the return oil hole is small.
【０００５】また、このような分離油が斜板室へ還給さ
れたしても、吸入ポートから斜板室内に流入した冷媒ガ
スは構造上の必然性から斜板室の周壁に沿って流動する
ため、とかく中心近傍の領域では冷媒ガスが希薄化され
るといった傾向がある。その結果、とくに駆動軸を支承
するラジアル軸受に潤滑不足が生じやすく、また、合理
化対策の一環として斜板を挟持するスラスト軸受に複合
型の滑り軸受の採用を試みたものでは、ころがり軸受に
みられるような大きな遊隙として存在しえない滑り面へ
の給油が極端に悪化することとなって、上記ラジアル軸
受ともども早期摩耗が避けられないといった問題もあ
る。Even if such separated oil is returned to the swash plate chamber, the refrigerant gas flowing into the swash plate chamber from the suction port flows along the peripheral wall of the swash plate chamber due to structural necessity. Anyway, the refrigerant gas tends to be diluted in the region near the center. As a result, in particular, radial bearings that support the drive shaft are liable to suffer insufficient lubrication. The oil supply to the sliding surface, which cannot exist as such a large play, is extremely deteriorated, and there is also a problem that early wear is inevitable with both the radial bearings.
【０００６】本発明の第１の解決課題は、分離油の還油
孔に配置されている弁装置を省去することであり、第２
の解決課題は、回転系軸受部の改替と潤滑不足の解消と
を同時に達成することである。A first problem to be solved by the present invention is to eliminate the valve device arranged in the return hole of the separated oil.
The problem to be solved is to simultaneously achieve the replacement of the rotary bearing and the elimination of insufficient lubrication.
【０００７】[0007]
【課題を解決するための手段】上記課題を解決する請求
項１記載の斜板式圧縮機は、前後に複数のボアを並設し
て結合部分に斜板室を形成した対のシリンダブロック
と、両シリンダブロックの中心軸孔にラジアル軸受を介
して嵌挿支承された駆動軸と、斜板室内の該駆動軸に装
着され、かつスラスト軸受を介して両シリンダブロック
に挟持された斜板と、該斜板にシューを介して係留し前
後のボア内を直動するピストンと、各ボアに対応する吸
入孔及び吐出孔を貫設した弁板と、外方域に吸入室、内
方域に吐出室を画設し、かつ吸入弁及び吐出弁を装備し
た該弁板を挟持して通しボルトによりシリンダブロック
の両外端を閉塞するハウジングとを備え、上記通しボル
トの周域に上記斜板室と上記吸入室とを連通する吸入通
路を開設した斜板式圧縮機において、上記吐出室と連な
って後部シリンダブロックの高圧領域に内装された油分
離室と、該油分離室の下方に連設された分離油回収用の
一次油溜室と、後部シリンダブロックの外端面又は弁板
に刻設された導油路を介して該一次油溜室と接続された
上記中心軸孔の後端部を含む主油溜室とを有し、該中心
軸孔内に配設された上記ラジアル軸受が滑り軸受で構成
されていることを特徴としている。A swash plate type compressor according to claim 1 which solves the above problems, is a pair of cylinder blocks in which a plurality of bores are provided in front and rear and a swash plate chamber is formed at a connecting portion, and a pair of cylinder blocks. A drive shaft fitted and supported by a radial bearing in a central shaft hole of the cylinder block; a swash plate mounted on the drive shaft in the swash plate chamber and sandwiched by both cylinder blocks via a thrust bearing; Pistons moored to the swash plate via shoes and moving directly in the front and rear bores, valve plates penetrating suction and discharge holes corresponding to each bore, suction chamber in the outer area, discharge in the inner area A housing that defines a chamber and holds the valve plate equipped with an intake valve and a discharge valve and closes both outer ends of the cylinder block with through bolts; and the swash plate chamber in the peripheral region of the through bolt. A swash plate type with an intake passage that communicates with the intake chamber In the compressor, an oil separation chamber that is connected to the discharge chamber and is installed in the high-pressure region of the rear cylinder block, a primary oil reservoir chamber that is continuously provided below the oil separation chamber for collecting separated oil, and a rear cylinder block A main oil reservoir chamber including a rear end portion of the central shaft hole connected to the primary oil reservoir chamber through an oil passage formed in an outer end surface of the valve plate or the valve plate. It is characterized in that the radial bearing arranged in the above is constituted by a slide bearing.
【０００８】請求項２記載の斜板式圧縮機は、上記ラジ
アル軸受の双方が滑り軸受、上記スラスト軸受の双方が
複合型の滑り軸受を構成され、上記駆動軸の軸心部には
両中心軸孔を連通する油孔が貫設されていることを特徴
としている。請求項３記載の斜板式圧縮機における上記
複合型のスラスト滑り軸受は、互いに対向する滑り面が
密合された内輪及び外輪からなり、上記シリンダブロッ
クと当接する外輪の滑り面には内周縁から外周縁に向う
適数条の潤滑溝が刻設され、該潤滑溝は内周面を軸方向
に延びる通溝と連接されていることを特徴としている。In a swash plate compressor according to a second aspect of the present invention, both of the radial bearings are sliding bearings, and both of the thrust bearings are complex sliding bearings, and both central shafts are provided at the center of the drive shaft. It is characterized in that an oil hole communicating with the hole is provided through. The compound type thrust slide bearing in the swash plate compressor according to claim 3 comprises an inner ring and an outer ring in which sliding faces facing each other are closely packed, and a sliding face of the outer ring contacting the cylinder block is formed from an inner peripheral edge. It is characterized in that a proper number of lubrication grooves facing the outer peripheral edge are engraved, and the lubrication grooves are connected to the through groove extending in the axial direction on the inner peripheral surface.
【０００９】好適な態様において、上記内輪及び外輪の
いずれか一方の滑り面に低摩擦樹脂皮膜が形成されてい
る。In a preferred embodiment, a low friction resin film is formed on the sliding surface of either the inner ring or the outer ring.
【００１０】[0010]
【作用】請求項１記載の斜板式圧縮機では、油分離機構
によって一次油溜室に回収された分離油が、導油路を介
して後部シリンダブロックの中心軸孔、とくに中立的圧
力雰囲気である同中心軸孔の後端部を含んで形成された
主油溜室に導入貯溜される。該中心軸孔内には駆動軸を
支承するラジアル滑り軸受が収嵌されており、駆動軸と
の嵌合細隙がもたらす絞り（減圧）作用が該貯溜油を誘
引し、斜板を挟持するスラスト軸受部に到達した油成分
は遠心力の助勢を得て軸受空隙から斜板室へと還元され
る。この場合、ラジアル滑り軸受自体が駆動軸との嵌合
細隙によって高圧冷媒ガスの逆流を阻止する実質的な弁
機能と供給油量の調整機能を果し、しかもこの嵌合細隙
は駆動軸の回転に基づいて常に油成分の流動を伴ってお
り、通常の弁手段にみられる詰りなどの不良現象は全く
生じない。In the swash plate compressor according to the first aspect of the present invention, the separated oil collected in the primary oil reservoir by the oil separation mechanism is passed through the oil passage to the central axial hole of the rear cylinder block, particularly in the neutral pressure atmosphere. It is introduced and stored in a main oil reservoir formed to include a rear end portion of a certain central shaft hole. A radial slide bearing for supporting the drive shaft is housed in the central shaft hole, and the throttling (pressure reduction) action caused by the fitting slit with the drive shaft attracts the stored oil to sandwich the swash plate. The oil component reaching the thrust bearing portion is assisted by centrifugal force and is reduced from the bearing gap to the swash plate chamber. In this case, the radial slide bearing itself fulfills a substantial valve function of blocking the reverse flow of high-pressure refrigerant gas and a function of adjusting the amount of supply oil by the fitting gap with the drive shaft, and this fitting gap also serves as the drive shaft. Since the oil component always flows due to the rotation of the valve, the defective phenomenon such as clogging found in the ordinary valve means does not occur at all.
【００１１】請求項２記載の斜板式圧縮機では、主油溜
室の貯溜油を駆動軸に穿設された油孔を介してフロント
側の中心軸孔へも供給することにより、斜板室へ還元さ
れる分離油をそのまま活用して、とかく不十分であった
ラジアル、スラスト両軸受の積極的な潤滑を果すことが
できるので、圧縮機の合理化に不可欠なこれら両軸受の
滑り軸受への転換も十分可能にすることができる。In the swash plate compressor according to the second aspect of the present invention, the stored oil in the main oil reservoir is supplied to the central shaft hole on the front side through the oil hole formed in the drive shaft, so that the swash plate chamber is supplied. Since the separated oil that is reduced can be used as it is, active lubrication of both radial and thrust bearings, which was inadequate, can be achieved, so conversion of these bearings to sliding bearings, which is essential for streamlining the compressor, is possible. Can be fully possible.
【００１２】[0012]
【実施例】以下、図に基づいて本発明の実施例を具体的
に説明する。図１、図２は片側５気筒の両頭斜板式圧縮
機を示すもので、前後に対設されたシリンダブロック
１、２の両端部は前後の弁板３、４を介してフロント及
びリヤのハウジング５、６により閉塞され、これらはボ
ルト挿通孔１ａ、２ａに挿通された複数本の通しボルト
７によって結合されている。シリンダブロック１、２の
結合部分には斜板室８が形成され、そこには両シリンダ
ブロック１、２の中心軸孔１ｂ、２ｂを貫通する駆動軸
９に固定された斜板１０が収容されている。上記シリン
ダブロック１、２には、５対のボア１１が、駆動軸９と
平行に、かつ駆動軸９を中心とする放射位置に形成さ
れ、各ボア１１には両頭形のピストン１２が嵌挿され
て、各ピストン１２は半球状のシュー１３を介して斜板
１０に係留されている。Embodiments of the present invention will be specifically described below with reference to the drawings. FIGS. 1 and 2 show a double-headed swash plate type compressor with five cylinders on each side. Both ends of cylinder blocks 1 and 2 which are opposed to each other at the front and rear are provided with front and rear housings via front and rear valve plates 3 and 4, respectively. Blocked by 5 and 6, these are connected by a plurality of through bolts 7 inserted into the bolt insertion holes 1a and 2a. A swash plate chamber 8 is formed in the connecting portion of the cylinder blocks 1 and 2, and a swash plate 10 fixed to a drive shaft 9 penetrating the central shaft holes 1b and 2b of both cylinder blocks 1 and 2 is housed therein. There is. Five pairs of bores 11 are formed in the cylinder blocks 1 and 2 in parallel with the drive shaft 9 and at a radial position around the drive shaft 9, and a double-headed piston 12 is fitted into each bore 11. Thus, each piston 12 is anchored to the swash plate 10 via a hemispherical shoe 13.
【００１３】上記フロント及びリヤのハウジング５、６
にはそれぞれ外方域に吸入室１４、１５が形成され、内
方域に吐出室１６、１７が形成されている。また、前後
の弁板３、４にはそれぞれ吸入室１４、１５から各ボア
１１内に低圧の冷媒ガスを吸入するための吸入孔１８、
１９と、各ボア１１から吐出室１６、１７内に圧縮され
た高圧の冷媒ガスを吐出するための吐出孔２０、２１と
が形成されている。さらに、弁板３、４のシリンダブロ
ック１、２側には吸入弁２２、２３が設けられ、弁板
３、４のハウジング５、６側には吐出弁２４、２５が設
けられている。The front and rear housings 5 and 6
The suction chambers 14 and 15 are formed in the outer regions of the respective units, and the discharge chambers 16 and 17 are formed in the inner regions thereof. Further, the front and rear valve plates 3 and 4 have suction holes 18 for sucking low-pressure refrigerant gas into the bores 11 from the suction chambers 14 and 15, respectively.
19 and discharge holes 20 and 21 for discharging the compressed high-pressure refrigerant gas from the bores 11 into the discharge chambers 16 and 17, respectively. Further, suction valves 22 and 23 are provided on the cylinder blocks 1 and 2 of the valve plates 3 and 4, and discharge valves 24 and 25 are provided on the housings 5 and 6 of the valve plates 3 and 4.
【００１４】上記リヤ側シリンダブロック２の上部には
後述するシェルと結合される台座部２６が設けられ、こ
の台座部２６には斜板室８に開口する図示しない吸入ポ
ートが配設されている。両シリンダブロック１、２から
弁板３、４を通して穿設された上記ボルト挿通孔１ａ、
２ａの一部（実施例においては３個）は、通しボルト７
との間の拡大遊隙によって実質的に斜板室８と吸入室１
４、１５とを連通する複数の吸入通路として形成されて
おり、上記吸入ポートから斜板室８に吸入された冷媒ガ
スがこの吸入通路を通って吸入室１４、１５内に導入さ
れる。なお、２７は軸封装置である。A pedestal portion 26, which is connected to a shell to be described later, is provided on the upper portion of the rear cylinder block 2, and a suction port (not shown) that opens into the swash plate chamber 8 is provided in the pedestal portion 26. The bolt insertion hole 1a formed through both the cylinder blocks 1 and 2 through the valve plates 3 and 4,
Part of 2a (three in the embodiment) is a through bolt 7
Due to the expanded play between the swash plate chamber 8 and the suction chamber 1
The refrigerant gas is formed as a plurality of suction passages that communicate with the suction chambers 4 and 15, and the refrigerant gas sucked from the suction port into the swash plate chamber 8 is introduced into the suction chambers 14 and 15 through the suction passages. In addition, 27 is a shaft sealing device.
【００１５】さて、本発明の特徴的構成の一つである油
分離機構について以下に詳述する。図２に示すように、
上記台座部２６にはシェル２８が取付けられ、その内部
にはサイクロン方式の油分離室３２が形成されている。
有底円孔状をなす該油分離室３２の上部には、座繰孔状
に加工された誘導部３２ａが該油分離室３２の周壁部へ
ほぼ接線状に開口されており、該誘導部３２ａの基端に
開口する通孔３３は両シリンダブロック１、２に形成さ
れた一対の吐出通路３４を経由して上記吐出室１６、１
７と連通されている。一方、該油分離室３２のやや下方
寄りには複数の貫孔３５ａをもつ隔板３５が嵌着され、
該隔板３５の下部領域と連なる隣室は該貫孔３５ａを介
して分離油を回収する一次油溜室３６に形成されてい
る。そして該一次油溜室３６はその底壁に穿設された通
孔３６ａが後部シリンダブロック２の外端面に開口３６
ｂされており、該開口３６ｂは同外端面に刻設された導
油路３８を介して中心軸孔２ｂに連通されている。ま
た、上記シェル２８を覆閉する蓋板２９には上記油分離
室３２の中心部へ突入延在する吐出管３７が固着され該
吐出管３７の外端は図示しない外部冷凍回路と連結され
ている。Now, the oil separation mechanism, which is one of the characteristic features of the present invention, will be described in detail below. As shown in FIG.
A shell 28 is attached to the pedestal portion 26, and a cyclone type oil separation chamber 32 is formed inside the shell 28.
In the upper part of the oil separation chamber 32 having a bottomed circular hole shape, a guide portion 32a processed into a counterbore hole is opened substantially tangentially to the peripheral wall portion of the oil separation chamber 32. A through hole 33 opened at the base end of 32a passes through a pair of discharge passages 34 formed in both cylinder blocks 1 and 2 to discharge chambers 16 and 1
It is in communication with 7. On the other hand, a partition plate 35 having a plurality of through holes 35a is fitted at a position slightly lower than the oil separation chamber 32,
An adjacent chamber connected to the lower region of the partition plate 35 is formed in a primary oil reservoir chamber 36 for collecting separated oil via the through hole 35a. The primary oil sump chamber 36 has a through hole 36a formed in the bottom wall thereof at the outer end surface of the rear cylinder block 2.
The opening 36b is communicated with the central shaft hole 2b through an oil passage 38 formed in the outer end surface of the opening 36b. Further, a discharge pipe 37 that extends into the center of the oil separation chamber 32 is fixed to a lid plate 29 that covers the shell 28, and the outer end of the discharge pipe 37 is connected to an external refrigeration circuit (not shown). There is.
【００１６】次いで本発明のさらに特徴的な構成である
回転系軸受部並びにその潤滑機構について説明する。す
なわち、上記通孔３６ａ及び導油路３８によって上記一
次油溜室３６と連通された中心軸孔２ｂの後端部は、リ
ヤハウジング６の中心領域を含んで中立的圧力雰囲気の
主油溜室Ｓとして形成され、該中心軸孔２ｂに該主油溜
室Ｓとは油路４８を有する隔壁４９を隔てて収嵌されて
いるラジアル軸受５１は、後述する弁機能をも兼備した
滑り軸受で構成されている。なお、本実施例は分離油の
回収還元と潤滑とを両立させて、両ラジアル軸受５０、
５１の滑り軸受化と共に、シリンダブロック１、２と斜
板１０との間に挟装されるスラスト軸受４０、４１も複
合型の滑り軸受で構成されている。そして前部のスラス
ト軸受４０を挟持する斜板１０の前部ボス並びに前部シ
リンダブロック１の支承部には、互いに対向するフラッ
トな受圧座が形成され、内輪４０ａ、外輪４０ｂが両受
圧座と密合することにより、該スラスト軸受は安定、か
つリジッドに挟持されている。Next, the rotating system bearing and its lubricating mechanism, which are the more characteristic features of the present invention, will be described. That is, the rear end portion of the central shaft hole 2b, which is communicated with the primary oil reservoir chamber 36 by the through hole 36a and the oil guide passage 38, includes the central region of the rear housing 6 and has a neutral pressure atmosphere in the main oil reservoir chamber. The radial bearing 51 which is formed as S and is housed in the central shaft hole 2b with a partition wall 49 having an oil passage 48 separated from the main oil reservoir S is a sliding bearing which also has a valve function to be described later. It is configured. In the present embodiment, both recovery and reduction of separated oil and lubrication are made compatible, and both radial bearings 50,
With the use of 51 as a sliding bearing, the thrust bearings 40 and 41 sandwiched between the cylinder blocks 1 and 2 and the swash plate 10 are also composed of compound type sliding bearings. Flat pressure receiving seats facing each other are formed on the front boss of the swash plate 10 that holds the front thrust bearing 40 and the support portion of the front cylinder block 1, and the inner ring 40a and the outer ring 40b are connected to both pressure receiving seats. By closely fitting, the thrust bearing is stable and is rigidly sandwiched.
【００１７】これに対し挟持手段を異にする後部のスラ
スト軸受４１には、アキシャル荷重を吸収する緩衝機能
が付与されている。すなわち斜板１０の後部ボスには比
較的大径の環状受圧座１０ａが形成されて、内輪４１ａ
はその外径近傍で該環状受圧座１０ａと衝接し、一方、
後部シリンダ２の支承部には比較的小径の環状受圧座２
ｃが形成されて、外輪４１ｂはその内径近傍で該環状受
圧座２ｃと衝接せしめられている。On the other hand, the rear thrust bearing 41 having a different clamping means is provided with a cushioning function for absorbing an axial load. That is, a relatively large-diameter annular pressure receiving seat 10a is formed on the rear boss of the swash plate 10, and the inner ring 41a
Collides with the annular pressure receiving seat 10a near its outer diameter, while
The bearing portion of the rear cylinder 2 has a relatively small diameter annular pressure receiving seat 2
c is formed, and the outer ring 41b is abutted against the annular pressure receiving seat 2c in the vicinity of its inner diameter.
【００１８】そして両スラスト軸受４０、４１は図５に
示すように、互いに対向する滑り面によって内輪４０
ａ、４１ａと外輪４０ｂ、４１ｂとが密合されており、
内輪４０ａ、４１ａの滑り面には例えばフッ素樹脂など
の低摩擦樹脂皮膜４５が形成されている。また、外輪４
０ｂ、４１ｂの滑り面には内周縁から外周縁に向う適数
条の潤滑溝４６が刻設され、該潤滑溝４６は内周面を軸
方向に延びる通溝４７と連接されている。As shown in FIG. 5, the thrust bearings 40 and 41 have inner surfaces of the inner ring 40 with sliding surfaces facing each other.
a, 41a and outer rings 40b, 41b are closely fitted,
A low-friction resin film 45 such as a fluororesin is formed on the sliding surfaces of the inner rings 40a and 41a. Also, the outer ring 4
An appropriate number of lubrication grooves 46 extending from the inner peripheral edge to the outer peripheral edge are engraved on the sliding surfaces of 0b and 41b, and the lubricating grooves 46 are connected to the through grooves 47 that extend in the inner peripheral surface in the axial direction.
【００１９】シリンダブロック１、２の両外側面には、
吸入通路を兼任しない上記ボルト挿通孔１ａ、２ａの少
なくとも一つと上記中心軸孔１ｂ、２ｂとを連通する導
溝３０が刻設され、該導溝３０と連通するボルト挿通孔
１ａ、２ａは図１に示すように斜板室８及び吸入室１
４、１５と絶縁されて独立した油路を形成している。本
実施例は上述のように構成されており、駆動軸９の回転
により斜板１０が回転されると、各ピストン１２がシリ
ンダボア１１内で往復動され、それによって冷媒ガスの
吸入、圧縮及び吐出が行われる。圧縮された高圧の冷媒
ガスは吐出室１６、１７から各吐出通路３４及び通孔３
３を介して油分離室３２に導入される。すなわち、通孔
３３から誘導部３２ａの基端部分に導かれた冷媒ガス
は、該誘導部３２ａに形成された側壁の案内によりほぼ
接線方向から円孔状をなす油分離室３２内に流入し、図
３に示す回転流によって与えられた遠心力により冷媒ガ
ス中の混在油粒は有効に分離される。なお、このような
油分離の過程を経ることによって冷媒ガスの脈動は物理
的に鎮静化されるので、きわめて安定した状態で冷凍回
路へと送給され、一方、冷媒ガスから分離された油成分
は油分離室３２の周壁を流下し、隔板３５に穿設された
貫孔３５ａから滴落して一次油溜室３６に回収され、さ
らには通孔３６ａ及び導油路３８を経由して主油溜室Ｓ
内に貯溜される。On both outer side surfaces of the cylinder blocks 1 and 2,
A guide groove 30 that communicates at least one of the bolt insertion holes 1a and 2a that also does not serve as a suction passage with the central shaft holes 1b and 2b is engraved, and the bolt insertion holes 1a and 2a that communicate with the guide groove 30 are shown in FIG. 1, the swash plate chamber 8 and the suction chamber 1
An oil passage is formed by being insulated from Nos. 4 and 15. The present embodiment is configured as described above, and when the swash plate 10 is rotated by the rotation of the drive shaft 9, each piston 12 is reciprocated in the cylinder bore 11, thereby sucking, compressing and discharging the refrigerant gas. Is done. The compressed high-pressure refrigerant gas is discharged from the discharge chambers 16 and 17 into each discharge passage 34 and the through hole 3.
3 is introduced into the oil separation chamber 32. That is, the refrigerant gas guided from the through hole 33 to the base end portion of the guide portion 32a flows into the oil separation chamber 32 having a circular hole shape from the tangential direction by the guide of the side wall formed in the guide portion 32a. The mixed oil particles in the refrigerant gas are effectively separated by the centrifugal force given by the rotating flow shown in FIG. Since the pulsation of the refrigerant gas is physically calmed down through such an oil separation process, it is sent to the refrigeration circuit in an extremely stable state, while the oil component separated from the refrigerant gas is supplied. Flows down the peripheral wall of the oil separation chamber 32, drops from the through hole 35a formed in the partition plate 35, is collected in the primary oil reservoir chamber 36, and further passes through the through hole 36a and the oil guide passage 38. Oil sump S
It is stored inside.
【００２０】該中心軸孔２ｂ内には駆動軸９を支承する
ラジアル滑り軸受５１が収嵌されており、駆動軸９との
嵌合細隙がもたらす絞り（減圧）作用が隔壁４９に貫設
された油路４８を介して該貯溜油を誘引し、斜板１０を
挟持するスラスト軸受４１に到達した油成分は遠心力の
助勢も得て軸受空隙から斜板室８へと還元される。この
場合、ラジアル滑り軸受５１自体が駆動軸９との嵌合細
隙によって高圧冷媒ガスの逆流を阻止する実質的な弁機
能と供給油量の調整機能を果し、しかもこの嵌合細隙は
駆動軸９の回転に基づいて常に油成分の流動を伴ってお
り、通常の弁手段にみられる詰りなどの不良現象は全く
生じない。A radial slide bearing 51 for supporting the drive shaft 9 is fitted in the central shaft hole 2b, and the partition 49 is penetrated by a throttling (pressure reduction) action provided by a fitting slit with the drive shaft 9. The stored oil is attracted through the oil passage 48 thus formed, and the oil component reaching the thrust bearing 41 holding the swash plate 10 is returned to the swash plate chamber 8 from the bearing gap with the help of centrifugal force. In this case, the radial plain bearing 51 itself fulfills a substantial valve function of preventing the reverse flow of the high-pressure refrigerant gas and a function of adjusting the amount of supplied oil by the fitting gap with the drive shaft 9, and this fitting gap is Due to the rotation of the drive shaft 9, the oil component always flows, and the defective phenomenon such as clogging found in the ordinary valve means does not occur at all.
【００２１】さて、本実施例においては通常、単に斜板
室８へ還元される分離油をそのまま活用して、とかく不
十分であったラジアル軸受５０、５１及びスラスト軸受
４０、４１の積極的な潤滑を果し、これらすべての軸受
要素を滑り軸受に転換して圧縮機の合理化に大きく寄与
することを狙いとしている。すなわち主油溜室Ｓに貯え
られた貯溜油の一部は、両シリンダブロック１、２の外
端面に刻設された導溝３０並びにこれら両導溝３０を連
通するとくに斜板室８及び吸入室１４、１５と絶縁され
たボルト挿通孔１ａ、２ａを介して前部シリンダブロッ
ク１の中心軸孔１ｂへと供給される。このため両中心軸
孔１ｂ、２ｂ内の油成分がラジアル軸受５０、５１から
スラスト軸受４０、４１を構成する外輪４０ｂ、４１ｂ
の通溝４７及び潤滑溝４６を潜通する間に、ラジアル軸
受５０、５１、スラスト軸受４０、４１の各滑り面は勿
論、フロント側の軸封装置２７も十分潤滑される。しか
もスラスト軸受４０、４１の相対的な滑り面のいずれか
一方（図は内輪側）に低摩擦樹脂皮膜４５を形成した
り、上記外輪４０ｂ、４１ｂの潤滑溝４６を図のように
駆動軸９の回転方向（矢印）の向きに湾曲せしめたもの
では、滑り面の良好な摺動と同時に油成分の流動がさら
に活発化される。In the present embodiment, normally, the separated oil that is simply reduced to the swash plate chamber 8 is used as it is, and the radial bearings 50 and 51 and the thrust bearings 40 and 41, which have been insufficient at all, are positively lubricated. The aim is to convert all of these bearing elements into sliding bearings and make a significant contribution to the rationalization of the compressor. That is, a part of the stored oil stored in the main oil storage chamber S is a guide groove 30 formed on the outer end surfaces of the cylinder blocks 1 and 2, and particularly the swash plate chamber 8 and the suction chamber that connect the guide grooves 30. It is supplied to the central shaft hole 1b of the front cylinder block 1 through bolt insertion holes 1a and 2a which are insulated from 14 and 15. Therefore, the oil components in both the central shaft holes 1b, 2b form the radial bearings 50, 51 to the outer rings 40b, 41b constituting the thrust bearings 40, 41.
While passing through the through groove 47 and the lubricating groove 46, the sliding surfaces of the radial bearings 50 and 51 and the thrust bearings 40 and 41 as well as the front shaft seal device 27 are sufficiently lubricated. Moreover, the low friction resin film 45 is formed on one of the relative sliding surfaces of the thrust bearings 40, 41 (inner ring side in the figure), and the lubricating groove 46 of the outer rings 40b, 41b is formed in the drive shaft 9 as shown in the figure. In the case of being curved in the direction of rotation (arrow), the flow of the oil component is further activated at the same time as the sliding surface slides well.
【００２２】したがって、合理化対策に欠かせないスラ
スト軸受４０、４１並びにラジアル軸受５０、５１の滑
り軸受への転換も、かかる潤滑機構の改善によって十分
可能とすることができる。なお、上記スラスト軸受４
０、４１の挟持手段の相違に基づいて機能する変動荷重
の吸収や不安定振動の抑制作用は、上記滑り軸受への転
換にかかわりなく発揮される。Therefore, the thrust bearings 40, 41 and the radial bearings 50, 51, which are indispensable for rationalization measures, can be converted into sliding bearings by improving the lubrication mechanism. The above thrust bearing 4
The function of absorbing fluctuating load and suppressing unstable vibration, which function based on the difference in the sandwiching means of 0 and 41, is exhibited regardless of conversion to the plain bearing.
【００２３】図４に示した他の実施例は、上記ボルト挿
通孔１ａ、２ａに代え、駆動軸９に穿設された油孔９ａ
を介して貯溜油をフロント側へ供給するものであり、前
実施例と同様に積極的な潤滑を果すことができる。な
お、上述の実施例は、導油路３８及び導溝３０をシリン
ダブロック１、２の外端面に刻設したが、これを弁板
３、４側に設けることも可能であり、また、中心軸孔２
ｂに形成された隔壁４９を省略し、駆動軸９の後端領域
を直ちに主油溜室Ｓとすることも可能である。さらに、
内外輪２枚構成からなるスラスト軸受４０、４１の輪体
を増設し、相対的滑り面の複式化を企図した形態で実施
することもできる。In another embodiment shown in FIG. 4, instead of the bolt insertion holes 1a and 2a, an oil hole 9a formed in the drive shaft 9 is used.
The stored oil is supplied to the front side via the, so that positive lubrication can be achieved as in the previous embodiment. In the above-described embodiment, the oil guide passage 38 and the guide groove 30 are formed on the outer end surfaces of the cylinder blocks 1 and 2, but they may be provided on the valve plates 3 and 4 side. Shaft hole 2
It is possible to omit the partition wall 49 formed in b and immediately use the rear end region of the drive shaft 9 as the main oil reservoir chamber S. further,
It is also possible to add a ring body of the thrust bearings 40 and 41 composed of two inner and outer rings to implement the relative sliding surfaces in a form intended to be doubled.
【００２４】[0024]
【発明の効果】以上、詳述したように本発明は、特許請
求の範囲に記載した構成を有するものであるから、以下
に掲記する優れた効果を奏する。 （１）請求項１記載の圧縮機では、高圧冷媒ガスから油
分離機構によって一次油溜室に回収された分離油は、中
心軸孔の後端部を含んで形成された主油溜室に導入貯溜
され、中心軸孔内に収嵌されたラジアル軸受及び斜板を
挟持するスラスト軸受を介して斜板室へ還元されるが、
滑り軸受で構成された該ラジアル軸受が、駆動軸との嵌
合細隙によって高圧冷媒ガスの逆流を阻止する弁機能と
供給油量の調整機能を果すので、従来還油孔に配設され
ていた弁手段を完全に省去することができる。 （２）請求項２記載の圧縮機では、両中心軸孔を導通す
ることにより、斜板室へ還元される分離油をそのまま活
用して前後の軸受要素を積極的に潤滑しうるので、ラジ
アル、スラスト両軸受の滑り軸受への転換を可能とし
て、合理化対策にこよなく貢献しうるとともに、圧縮機
の信頼性を格段に向上させることができる。 （３）請求項３及び４記載の圧縮機では、両軸受の滑り
面における一層円滑な摺動が期待できる。As described above in detail, since the present invention has the constitution described in the claims, it has the following excellent effects. (1) In the compressor according to claim 1, the separated oil recovered from the high-pressure refrigerant gas in the primary oil reservoir by the oil separation mechanism is stored in the main oil reservoir formed including the rear end of the central shaft hole. It is introduced and stored, and is returned to the swash plate chamber through the radial bearing fitted in the central shaft hole and the thrust bearing that sandwiches the swash plate.
Since the radial bearing composed of a slide bearing has a valve function of preventing backflow of high-pressure refrigerant gas and a function of adjusting the amount of supplied oil by a fitting slit with a drive shaft, the radial bearing is conventionally arranged in the return oil hole. The valve means can be eliminated altogether. (2) In the compressor according to the second aspect of the present invention, by conducting both central shaft holes, the separated oil reduced to the swash plate chamber can be utilized as it is to positively lubricate the front and rear bearing elements. It is possible to convert both thrust bearings to plain bearings, which can contribute not only to rationalization measures, but also to significantly improve the reliability of the compressor. (3) In the compressors according to claims 3 and 4, smoother sliding on the sliding surfaces of both bearings can be expected.
【図１】本発明の実施例に係る両頭斜板式圧縮機の全容
を示す断面図。FIG. 1 is a cross-sectional view showing the entire contents of a double-headed swash plate compressor according to an embodiment of the present invention.
【図２】油分離と分離油の還給構成を示すシリンダブロ
ックの一部断面側面図。FIG. 2 is a partial cross-sectional side view of a cylinder block showing an oil separation and a separated oil return configuration.
【図３】油分離室を示す平面図。FIG. 3 is a plan view showing an oil separation chamber.
【図４】本発明の他の実施例を示す圧縮機の断面図。FIG. 4 is a sectional view of a compressor showing another embodiment of the present invention.
【図５】本発明の実施例に係るスラスト軸受を示し、
（ａ）は断面正面図、（ｂ）は滑り面の側面図。FIG. 5 shows a thrust bearing according to an embodiment of the present invention,
(A) is a sectional front view and (b) is a side view of a sliding surface.
１は前部シリンダブロック、２は後部シリンダブロッ
ク、１ａ、２ａはボルト挿通孔、１ｂ、２ｂは中心軸
孔、３、４は弁板、５はフロントハウジング、６はリヤ
ハウジング、７は通しボルト、８は斜板室、９は駆動
軸、９ａは油孔、１０は斜板、１４、１５は吸入室、２
２、２３は吸入弁、３０は導溝、３２は油分離室、３６
は一次油溜室、３８は導油路、４０、４１はスラスト軸
受、４０ａ、４１ａは内輪、４０ｂ、４１ｂは外輪、４
５は低摩擦樹脂皮膜、４６は潤滑溝、４７は通溝、Ｓは
主油溜室1 is a front cylinder block, 2 is a rear cylinder block, 1a and 2a are bolt insertion holes, 1b and 2b are central shaft holes, 3 and 4 are valve plates, 5 is a front housing, 6 is a rear housing, and 7 is a through bolt. , 8 is a swash plate chamber, 9 is a drive shaft, 9a is an oil hole, 10 is a swash plate, 14 and 15 are suction chambers, 2
2, 23 are suction valves, 30 is a guide groove, 32 is an oil separation chamber, 36
Is a primary oil storage chamber, 38 is an oil guide passage, 40 and 41 are thrust bearings, 40a and 41a are inner rings, 40b and 41b are outer rings, 4
5 is a low friction resin film, 46 is a lubricating groove, 47 is a through groove, and S is a main oil reservoir.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 川村 尚登 愛知県刈谷市豊田町２丁目１番地 株式会 社豊田自動織機製作所内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Naoto Kawamura 2-chome, Toyota-cho, Kariya city, Aichi stock company Toyota Industries Corp.
Claims (4)
板室を形成した対のシリンダブロックと、両シリンダブ
ロックの中心軸孔にラジアル軸受を介して嵌挿支承され
た駆動軸と、斜板室内の該駆動軸に装着され、かつスラ
スト軸受を介して両シリンダブロックに挟持された斜板
と、該斜板にシューを介して係留し前後のボア内を直動
するピストンと、各ボアに対応する吸入孔及び吐出孔を
貫設した弁板と、外方域に吸入室、内方域に吐出室を画
設し、かつ吸入弁及び吐出弁を装備した該弁板を挟持し
て通しボルトによりシリンダブロックの両外端を閉塞す
るハウジングとを備え、上記通しボルトの周域に上記斜
板室と上記吸入室とを連通する吸入通路を開設した斜板
式圧縮機において、上記吐出室と連なって後部シリンダ
ブロックの高圧領域に内装された油分離室と、該油分離
室の下方に連設された分離油回収用の一次油溜室と、後
部シリンダブロックの外端面又は弁板に刻設された導油
路を介して該一次油溜室と接続された上記中心軸孔の後
端部を含む主油溜室とを有し、該中心軸孔内に配設され
た上記ラジアル軸受が滑り軸受で構成されていることを
特徴とする斜板式圧縮機。1. A pair of cylinder blocks in which a plurality of bores are arranged side by side in the front and rear to form a swash plate chamber in a coupling portion, and a drive shaft fitted and supported by radial bearings in central shaft holes of both cylinder blocks. A swash plate mounted on the drive shaft in the swash plate chamber and sandwiched by both cylinder blocks via thrust bearings; and a piston moored to the swash plate via shoes and directly moving in the front and rear bores; A valve plate having a suction hole and a discharge hole corresponding to each bore, a suction chamber in the outer region and a discharge chamber in the inner region are defined, and the valve plate equipped with the suction valve and the discharge valve is sandwiched. And a housing that closes both outer ends of the cylinder block with through bolts, and the suction passage that opens the swash plate chamber and the suction chamber in the peripheral area of the through bolt is opened. High pressure area of the rear cylinder block connected to the chamber Through an oil separation chamber, a primary oil storage chamber for collecting separated oil that is continuously provided below the oil separation chamber, and an oil passage formed in the outer end surface of the rear cylinder block or the valve plate. And a main oil reservoir including a rear end portion of the central shaft hole connected to the primary oil reservoir, and the radial bearing arranged in the central shaft hole is constituted by a slide bearing. A swash plate type compressor characterized in that.
スラスト軸受の双方が複合型の滑り軸受で構成され、上
記駆動軸の軸心部には両中心軸孔を連通する油孔が貫設
されていることを特徴とする請求項１記載の圧縮機。2. Both of the radial bearings are constituted by sliding bearings, and both of the thrust bearings are constituted by complex type sliding bearings, and an oil hole communicating with both central shaft holes is formed in the shaft center portion of the drive shaft. The compressor according to claim 1, wherein the compressor is provided.
向する滑り面が密合された内輪及び外輪からなり、上記
シリンダブロックと当接する外輪の滑り面には内周縁か
ら外周縁に向う適数条の潤滑溝が刻設され、該潤滑溝は
内周面を軸方向に延びる通溝と連接されていることを特
徴とする請求項２記載の圧縮機。3. The composite type thrust slide bearing is composed of an inner ring and an outer ring in which sliding surfaces facing each other are closely packed, and the sliding surface of the outer ring contacting the cylinder block has a proper number from the inner peripheral edge to the outer peripheral edge. The compressor according to claim 2, wherein a linear lubrication groove is engraved, and the lubrication groove is connected to a through groove extending in the axial direction on the inner peripheral surface.
に低摩擦樹脂皮膜が形成されていることを特徴とする請
求項３記載の圧縮機。4. A compressor according to claim 3, wherein a low-friction resin film is formed on the sliding surface of either the inner ring or the outer ring.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP07772195A JP3144616B2 (en) | 1995-04-03 | 1995-04-03 | Swash plate compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP07772195A JP3144616B2 (en) | 1995-04-03 | 1995-04-03 | Swash plate compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH08270553A true JPH08270553A (en) | 1996-10-15 |
| JP3144616B2 JP3144616B2 (en) | 2001-03-12 |
Family
ID=13641766
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP07772195A Expired - Fee Related JP3144616B2 (en) | 1995-04-03 | 1995-04-03 | Swash plate compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3144616B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7976288B2 (en) | 2006-05-19 | 2011-07-12 | Kabushiki Kaisha Toyota Jidoshokki | Refrigerant gas compressor |
| KR101488284B1 (en) * | 2009-12-02 | 2015-02-02 | 기아자동차주식회사 | Structure for supporting swash plate type compressor in order to enhancing lubrication |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105804970A (en) * | 2014-12-31 | 2016-07-27 | 华域三电汽车空调有限公司 | Compressor piston |
-
1995
- 1995-04-03 JP JP07772195A patent/JP3144616B2/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7976288B2 (en) | 2006-05-19 | 2011-07-12 | Kabushiki Kaisha Toyota Jidoshokki | Refrigerant gas compressor |
| KR101488284B1 (en) * | 2009-12-02 | 2015-02-02 | 기아자동차주식회사 | Structure for supporting swash plate type compressor in order to enhancing lubrication |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3144616B2 (en) | 2001-03-12 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |