JPH01227890A - Rotary compressor - Google Patents

Abstract

PURPOSE:To elongate the sealing distance between the opposing end faces of a roller and both bearings and improve the efficiency by forming approximately circular grooves of which each one end is communicated with the internal peripheral part of the roller and the other end is near that internal peripheral part, on each of the opposing end faces of the roller opposed to a main bearing and a supplementary bearing. CONSTITUTION:One end face 19a of a roller 19 is opposed to a main bearing 7 and the other end face 19b is to a supplementary bearing 8. A plurality of circular grooves 20 to 23 are formed on one end face 19a and communicated at one ends with the internal periphery of the roller 19 and extend to the other ends near the internal periphery of said roller 19, that is, not communicated therewith. The opposite end face 19b of the roller 19 has the same number and the same form of the grooves as on the end face 19a. When the grooves 20 to 23 are supplied with lubricating oil, since the end parts 20b to 23b are not communicated with the internal periphery of the roller, the pressure rises due to the self-revolution action of the roller 19, whereby maintaining the clearance between each of the bearing and the roller 19 equal, elongating the sealing distance due to the circular form and improving the efficiency.

Description

【発明の詳細な説明】 産業上の利用分野 本発明は、冷凍サイクル等に使用する回転式圧縮機に関
し、特に体積効率が良好な機械部の構成に係わる。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a rotary compressor used in a refrigeration cycle or the like, and particularly relates to the configuration of a mechanical part with good volumetric efficiency.

従来の技術 従来の構成を第３図、第４図、第５図、第６図を用いて
説明する。Prior Art A conventional configuration will be explained with reference to FIGS. 3, 4, 5, and 6.

１は密閉ケーシング、２は電動機部であり、シャフト３
を介してシリンダ４、ローラ５、ベーンｅ、主軸受子、
副軸受８により構成される機械部本体９と連結している
。シャフト３は主軸３ａ。1 is a sealed casing, 2 is an electric motor section, and shaft 3
Through the cylinder 4, roller 5, vane e, main bearing,
It is connected to a mechanical part main body 9 constituted by a sub-bearing 8. The shaft 3 is a main shaft 3a.

副軸３ｂ、クランク３ｃよシなる。また、シャフト３の
中心には穴３ｅが形成されると共にクランク３Ｃには給
油孔３１、給油溝３ｑが設けられている。１ｏはベーン
背面に設けられたスプリングである。１１ａ、１１ｂは
シリンダ４内で、ローラ５、ベーン６、主軸受７、副軸
受８により構成される吸入室と圧縮室である。ローラ６
の主軸受７、副軸受８と対向するそれぞれの端面ｓａ、
ｓｂの内周側にはテーパｓｃ、ｓｄが設けられている。The subshaft 3b and the crank 3c are the same. Further, a hole 3e is formed in the center of the shaft 3, and an oil supply hole 31 and an oil supply groove 3q are provided in the crank 3C. 1o is a spring provided on the back side of the vane. Reference numerals 11a and 11b are a suction chamber and a compression chamber in the cylinder 4, which are constituted by a roller 5, a vane 6, a main bearing 7, and a sub-bearing 8. roller 6
Each end face sa facing the main bearing 7 and the sub-bearing 8,
Tapers sc and sd are provided on the inner peripheral side of sb.

１２は、シャフト３と連結する給油機構である。12 is an oil supply mechanism connected to the shaft 3.

１３は吸入管であシ、副軸受８、シリンダ４の吸入通路
１４を介して吸入室１１ａと連通している。Reference numeral 13 denotes a suction pipe, which communicates with the suction chamber 11a via the auxiliary bearing 8 and the suction passage 14 of the cylinder 4.

１６は吐出孔であり吐出弁１６を介して密閉ケーシング
１内と連通している。１７は吐出管であシ密閉ケーシン
グ１内に開放している。１８は潤滑油である。Reference numeral 16 denotes a discharge hole, which communicates with the inside of the sealed casing 1 via the discharge valve 16. Reference numeral 17 is a discharge pipe which opens into the sealed casing 1. 18 is lubricating oil.

次に回転式圧縮機の圧縮機構について説明する。Next, the compression mechanism of the rotary compressor will be explained.

冷却システム（図示せず）からの冷媒ガスは、吸入管１
３、吸入孔１４より導かれシリンダ４内の吸入室１１ａ
に至る。吸入室１１ａに至った冷媒ガスは、シャフト３
のクランク３Ｃに回転自在に収納されたローラ５とベー
ン６によシ仕切られた圧縮室１１ｂで、電動機部２の回
転に伴うシャフト３の回転運動により漸次圧縮される。Refrigerant gas from the cooling system (not shown) is supplied to the suction pipe 1
3. Suction chamber 11a inside cylinder 4 guided from suction hole 14
leading to. The refrigerant gas that has reached the suction chamber 11a is transferred to the shaft 3
The compression chamber 11b is partitioned by a roller 5 and a vane 6, which are rotatably housed in the crank 3C, and is gradually compressed by the rotational movement of the shaft 3 as the electric motor section 2 rotates.

圧縮された冷媒ガスは、吐出孔１６、吐出弁１６を介し
て密閉ケーシング１内に一旦吐出された後、吐出管１７
を介し冷却システムに吐出される。The compressed refrigerant gas is once discharged into the sealed casing 1 through the discharge hole 16 and the discharge valve 16, and then through the discharge pipe 17.
to the cooling system.

又、冷媒の溶は込んだ密閉ケーシング１内の高圧の潤滑
油１８は、給油機構１２によシシャフト３の穴３ｅに供
給され、主軸受７と副軸受８との摺動部に供給されると
共に、給油孔３ｆ、給油溝３ｑよりクランク３Ｃとロー
２６の内周側に供給され、差圧によりローラ端面ｓａ　
、ｓｂを潤滑した後、吸入室１１ａ１圧縮室１１ｂに至
り、その後吐出孔１６より密閉ケーシング１内に吐出さ
れ、密閉ケーシング１の下部に戻る。Further, the high-pressure lubricating oil 18 in the sealed casing 1 filled with refrigerant is supplied to the hole 3e of the shaft 3 by the oil supply mechanism 12, and is supplied to the sliding part between the main bearing 7 and the sub-bearing 8. At the same time, the oil is supplied from the oil supply hole 3f and the oil supply groove 3q to the inner peripheral side of the crank 3C and the row 26, and the roller end surface sa is supplied by the differential pressure.
, sb, it reaches the suction chamber 11a1 and the compression chamber 11b, is then discharged into the sealed casing 1 from the discharge hole 16, and returns to the lower part of the sealed casing 1.

このとき、ローラ６の端面ｓａ　、ｓｂには、テーパｓ
ａ、ｓｄが設けられている為、高い圧力の潤滑油が内径
側より外径側に向い断面先細のクサビ形通路を流れるこ
ととなシ、両端面ｓａ　、　ｓｂのそれぞれでの油圧力
がバランスしその結果ローラ５と主軸受７、副軸受８間
のクリアランスδ６とδｂがδ６＝δｂとなる様にロー
ラ６が保持される。ところで、ローラ端面ｓａ、ｓｂを
介して、クランク３Ｃ側から吸入室１１ａ、圧縮室１１
ｂに流入する冷媒の溶は込んだ潤滑油の量は、クリアラ
ンスの３乗に比例する。従って、δ２＋δｂ＝一定の場
合、流入する量はδユ＝δｂのときに最小となシ、その
結果、テーパｓｃ、ｓｄを設けることによシ、体積効率
が良好で効率の高い圧縮機が提供される。At this time, the end surfaces sa and sb of the roller 6 have tapers s
Since a and sd are provided, high-pressure lubricating oil does not flow from the inner diameter side to the outer diameter side through a wedge-shaped passage with a tapered cross section, and the hydraulic pressure at both end surfaces sa and sb is balanced. As a result, the roller 6 is held such that the clearances δ6 and δb between the roller 5, the main bearing 7, and the auxiliary bearing 8 become δ6=δb. By the way, the suction chamber 11a and the compression chamber 11 are connected from the crank 3C side via the roller end surfaces sa and sb.
The amount of lubricating oil dissolved in the refrigerant flowing into b is proportional to the cube of the clearance. Therefore, when δ2+δb=constant, the amount of inflow is the minimum when δu=δb.As a result, by providing the tapers sc and sd, a highly efficient compressor with good volumetric efficiency can be provided. be done.

例えば、実公昭６１−２０３１７号公報にて示される。For example, it is shown in Japanese Utility Model Publication No. 61-20317.

発明が解決しようとする課題 この様な従来の構造では、冷凍用の気筒容積の小さい小
型圧縮機の様にローラの（外径−肉径）／２で示される
肉厚が薄く、運転時の高圧圧力と低圧圧力の比（圧縮比
）が高い圧縮機では、テーパを設けてローラの端面と主
軸受及びローラと副軸受のクリアランスを等しくできて
も、実際には全周に亘って設けられたテーパ部のクリア
ランスはテーパ量だけ広がり又、テーパのない平坦面の
シール距離が全周で短かくなるため、吸入室や圧縮室へ
の冷媒の溶は込んだ潤滑油の流入量が増加し結局テーパ
を設けても体積効率があまり向上しないとの課題があっ
た。Problems to be Solved by the Invention In such a conventional structure, the wall thickness of the roller, expressed as (outer diameter - wall diameter)/2, is thin, such as in a small compressor with a small cylinder capacity for refrigeration, and the wall thickness during operation is small. In a compressor with a high ratio of high pressure to low pressure (compression ratio), even if a taper is provided to equalize the clearance between the roller end face and the main bearing, and between the roller and the sub-bearing, in reality it is not provided all around the circumference. The clearance of the tapered part increases by the taper amount, and the sealing distance of the non-tapered flat surface becomes shorter around the entire circumference, so the amount of lubricating oil with dissolved refrigerant flowing into the suction chamber and compression chamber increases. In the end, there was a problem in that even if a taper was provided, the volumetric efficiency did not improve much.

本発明は上記従来例の欠点を解消するものであり、小型
でローラの肉厚が薄い圧縮機においても吸入室や圧縮室
への冷媒の溶は込んだ潤滑油の流入量を最小に抑えるこ
とを目的としている。The present invention solves the above-mentioned drawbacks of the conventional example, and it is possible to minimize the amount of lubricating oil containing refrigerant dissolved into the suction chamber and compression chamber even in a compressor that is small and has thin rollers. It is an object.

課題を解決するための手段 本発明は、ローラの端面のそれぞれに、一端がローラの
内周側に連通し且つ他端がローラの内周の近傍に至る略
円弧状の溝を設けたものである。Means for Solving the Problems The present invention provides a substantially arc-shaped groove on each end face of the roller, one end communicating with the inner circumference of the roller and the other end reaching near the inner circumference of the roller. be.

作　　用 本発明は上記した構成により、ローラの公転・自転運動
に伴い潤滑油が溝内に封じ込められて圧力が上昇し、こ
の油圧力が両端面でバランスするためにローラと主軸受
及び副軸受間のクリアランスδ４とδｂがδ２＝δｂに
保持される。このとき、溝が全周に亘って設けられてお
らないこと及び溝巾をテーパの巾よシ細くできることに
よりシール距離がテーパを設ける場合より長くなり、そ
の結果圧縮室や吸入室へ流入するオイル量が減少する。Effect: With the above-described configuration, the lubricating oil is confined in the groove and the pressure increases as the roller revolves and rotates, and this oil pressure is balanced on both end faces, so that the roller, main bearing, and sub bearing The clearance between δ4 and δb is maintained at δ2=δb. At this time, since the groove is not provided all around the circumference and the groove width can be made narrower than the width of the taper, the sealing distance becomes longer than when a taper is provided, and as a result, the oil flowing into the compression chamber and suction chamber quantity decreases.

実施例 以下本発明の一実施例を第１図、第２図にて説明する。Example An embodiment of the present invention will be described below with reference to FIGS. 1 and 2.

尚、従来例と同一部分は同一符号を付し詳細な説明を省
略する。１９はローラであり、従来と同様にシャフトの
クランク３Ｃに回転自在に収納されている。また、ロー
ラ１９の端面１９ａ。Note that the same parts as in the conventional example are given the same reference numerals and detailed explanations are omitted. A roller 19 is rotatably housed in the crank 3C of the shaft as in the conventional case. Also, the end surface 19a of the roller 19.

１９ｂには、略円弧状の溝２０，２１，２２．２３及び
２４°、２５．２６．２７が同数だけ設けられている。The same number of substantially arcuate grooves 20, 21, 22, 23, 24°, 25, 26, 27 are provided in 19b.

溝２０〜２７は、一端２０ａ〜２７ａが、ローラ１９の
内周側に連通し且つ他端２ｏｂ〜２７ｂがローラ６の内
周近傍に至シ内周側とは連通しない略円弧状の形状をし
ている。The grooves 20 to 27 have a generally arcuate shape in which one ends 20a to 27a communicate with the inner circumferential side of the roller 19, and the other ends 2ob to 27b communicate with the inner circumferential side of the roller 6, but do not communicate with the inner circumferential side. are doing.

従来と同様に、冷媒ガスは、吸入管１３よシ吸入室１１
ａに吸入され圧縮室１１ｂにて圧縮された後吐出孔１６
、密閉ケーシング１を介して吐出管１７を介して吐出さ
れる。As in the past, the refrigerant gas flows through the suction pipe 13 and into the suction chamber 11.
a, and after being compressed in the compression chamber 11b, the discharge hole 16
, is discharged through the closed casing 1 through the discharge pipe 17.

又、冷媒の溶は込んだ潤滑油１８も従来と同様にローラ
１９の内周側に供給され、差圧によシローラの端面１９
ａ、１９ｂを潤滑した後、吸入室１１ａ１圧縮室１ｂを
介して密閉ケーシング１の下部に戻る。In addition, the lubricating oil 18 containing the refrigerant is also supplied to the inner circumferential side of the roller 19 as in the conventional case, and the end surface 19 of the roller 19 is heated by the differential pressure.
After lubricating the parts a and 19b, it returns to the lower part of the sealed casing 1 via the suction chamber 11a1 and the compression chamber 1b.

この圧縮行程においてローラ１９は、クランク３ｃの回
転に伴い公転運動をすると共に、ローラ１９がクランク
３ｃに回転自在に収納されていることによシ自転運動を
行なう。また、溝２０〜２７には潤滑油が流入し、端部
２０ｂ〜２７ｂが内周側に連通していないため、ロー２
１９の公転運動と自転運動により潤滑油は溝２０〜２７
内に封じ込められて圧力が上昇する。これが溝２０〜２
７の全てにおいて発生するために端面１９ａと１９ｂに
作用する油圧力がバランスし、従来と同様にクリアラン
スδ６．δｂはδ６＝δｂに保持される。In this compression stroke, the roller 19 makes a revolution movement as the crank 3c rotates, and also makes an autorotation movement because the roller 19 is rotatably housed in the crank 3c. In addition, since lubricating oil flows into the grooves 20 to 27 and the ends 20b to 27b do not communicate with the inner circumferential side, the row 2
The lubricating oil flows through the grooves 20 to 27 due to the orbital and rotational movements of 19.
It becomes trapped inside and the pressure increases. This is groove 20-2
7, the hydraulic pressures acting on the end faces 19a and 19b are balanced, and the clearance δ6. δb is maintained at δ6=δb.

そして、溝２０〜２７が全周に亘って設けられておらず
一部だけであるため、従来の如く全周にテーパが設けら
れている場合よりシール距離が長くなシ小型で運転圧縮
比の高い圧縮機においても吸入室１１ａ１圧縮室１１ｂ
への冷媒を含んだ潤滑油の流入量が減少する。Since the grooves 20 to 27 are not provided all the way around, but only in a part, the sealing distance is longer than in the conventional case where tapers are provided all around the circumference. Even in a high compressor, the suction chamber 11a1 compression chamber 11b
The amount of lubricating oil containing refrigerant flowing into the tank decreases.

又、溝２０〜２７部においても、溝の深さで潤滑油の保
油量を制御できるため、従来のテーパ部の幅に比べて溝
幅が狭くでき従ってシール距離が長くできる。Furthermore, since the amount of lubricating oil retained in the grooves 20 to 27 can be controlled by the depth of the groove, the groove width can be narrower than the width of the conventional tapered portion, and the sealing distance can therefore be increased.

更に、溝２０〜２７が略円弧状で且つ端部２０ａ〜２７
ａ及び２０ｂ〜２７ｂが外周より離れているために、溝
２０〜２７とローラ１９の外周の距離は平均的にテーパ
の場合に比べて長くとることができ、流入量を減少する
ことができる。Further, the grooves 20 to 27 are approximately arcuate, and the ends 20a to 27 are substantially arcuate.
Since the grooves a and 20b to 27b are apart from the outer periphery, the distance between the grooves 20 to 27 and the outer periphery of the roller 19 can be longer on average than in the case of a taper, and the amount of inflow can be reduced.

従って、ローラの端面１ｓａ、１９ｂを潤滑するのに必
要な最低限の潤滑油を供給することができ、この結果体
積効率が良好で効率の高い圧縮機を提供できる。Therefore, the minimum amount of lubricating oil necessary to lubricate the end surfaces 1sa and 19b of the rollers can be supplied, and as a result, a highly efficient compressor with good volumetric efficiency can be provided.

発明の効果 以上の説明から明らかな様に本発明は、シリンダとシリ
ンダの端面に固定された主軸受及び副軸受と、主軸受及
び副軸受内を回転摺動し且つクランクを有するシャフト
と、シャフトのクランクに回転自在に収納されたローラ
と、ローラに当接し且つシリンダに設けられた溝内を往
復運動するベーンと、ローラの主軸受及び副軸受と対向
する端面のそれぞれに、一端がローラの内周側に連通し
且つ他端がローラの内周側の近傍に至る略円弧状の溝を
同数だけ設けたものであるから、ローラの端面と主軸受
及び副軸受間のクリアランスが等しくなると共に、シー
ル距離が長くなシ、体積効率が良好で効率の高い圧縮機
を供給することができる。Effects of the Invention As is clear from the above description, the present invention comprises a cylinder, a main bearing and a sub-bearing fixed to the end face of the cylinder, a shaft that rotates and slides within the main bearing and the sub-bearing and has a crank, and a shaft. a roller rotatably housed in the crank; a vane that contacts the roller and reciprocates in a groove provided in the cylinder; Since the same number of substantially arc-shaped grooves are provided that communicate with the inner circumferential side and whose other ends reach near the inner circumferential side of the roller, the clearance between the end face of the roller and the main bearing and the sub-bearing becomes equal. , a compressor with a long sealing distance, good volumetric efficiency, and high efficiency can be provided.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図は本発明の一実施例を示す回転式圧縮機のローラ
の正面図、第２図は本発明の機械部の拡大断面図、第３
図は従来の回転式圧縮機の縦断面図、第４図は第３図の
ＩＶ　−ＩＩ／’線における矢視図、第６図は第３図の
機械部の拡大断面図、第６図は従来のローラの正面図で
ある。 ３・・・・・・シャフト、３ｃ・・・・・・クランク、
４・・・・・・シリンダ、６・・・・・・ベーン、７・
・・・・・主軸受、８・・・・・・副Ｍ、１９・・・・
・・ローラ、１９ａ、１９ｂ・・川・ローラ端面、２０
，２１．２２，２３，２４，２５゜２６．２７・甲・・
溝、２０ａ、２１ａ、２２ａ。 ２３ａ　、２４ａ　、２５ａ　、２６ａ　、２’７ａ・
・・・・・溝の一端、２０ｂ　、　２１　ｂ　、　２２
ｂ　、　２３ｂ　、　２４ｂ。 ２ｓｂ、２ｅｂ、２７ｂ・・・・・・溝の他端。 代理人の氏名　弁理士　中　尾　敏　男　はが１名ｌ９
・−ローラ 、　　　ｌ　　図　　　　　　　　　　　　ｚｏｈｚ′
ｂ、ｚｓｂ、ｚｓｂ−４＋７）　　４１′　鳥第２図 、？ｆ 第３図 び 第４図FIG. 1 is a front view of a roller of a rotary compressor showing an embodiment of the present invention, FIG. 2 is an enlarged sectional view of the mechanical part of the present invention, and FIG.
The figure is a vertical sectional view of a conventional rotary compressor, FIG. 4 is a view along the line IV-II/' in FIG. 3, and FIG. 6 is an enlarged sectional view of the mechanical part in FIG. 3. is a front view of a conventional roller. 3...Shaft, 3c...Crank,
4...Cylinder, 6...Vane, 7.
...Main bearing, 8...Sub-M, 19...
...Rollers, 19a, 19b...River roller end face, 20
,21.22,23,24,25゜26.27・A...
Grooves, 20a, 21a, 22a. 23a, 24a, 25a, 26a, 2'7a・
...One end of the groove, 20b, 21b, 22
b, 23b, 24b. 2sb, 2eb, 27b...the other end of the groove. Name of agent: Patent attorney Toshi Nakao (1 person)
・-Laura, l Figure zohz'
b, zsb, zsb-4+7) 41' Bird 2nd figure, ? f Figures 3 and 4

Claims (1)

【特許請求の範囲】[Claims] シリンダと、前記シリンダの端面に固定された主軸受及
び副軸受と、前記主軸受及び副軸受内を回転摺動し且つ
クランクを有するシャフトと、前記シャフトのクランク
に回転自在に収納されたローラと、前記ローラに当接し
且つ前記シリンダに設けられた溝内を往復摺動するベー
ンと、前記ローラの前記主軸受及び副軸受と対向する端
面のそれぞれに、一端が前記ローラの内周側に連通し且
つ他端が前記ローラの内周側の近傍に至る略円弧状の溝
とを有した回転式圧縮機。a cylinder, a main bearing and a sub-bearing fixed to an end face of the cylinder, a shaft that rotates and slides within the main bearing and the sub-bearing and has a crank, and a roller that is rotatably housed in the crank of the shaft. , a vane that comes into contact with the roller and slides back and forth in a groove provided in the cylinder, and one end of each of the end faces of the roller that faces the main bearing and the sub-bearing that communicates with the inner peripheral side of the roller. and a substantially arc-shaped groove whose other end reaches near the inner peripheral side of the roller.