JPH0441989A - Rotation shaft for rotary compressor - Google Patents
Rotation shaft for rotary compressorInfo
- Publication number
- JPH0441989A JPH0441989A JP14957790A JP14957790A JPH0441989A JP H0441989 A JPH0441989 A JP H0441989A JP 14957790 A JP14957790 A JP 14957790A JP 14957790 A JP14957790 A JP 14957790A JP H0441989 A JPH0441989 A JP H0441989A
- Authority
- JP
- Japan
- Prior art keywords
- diameter
- rotating shaft
- rotation shaft
- lower bearing
- thrust
- 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.)
- Pending
Links
- 230000006835 compression Effects 0.000 claims description 11
- 238000007906 compression Methods 0.000 claims description 11
- 239000003507 refrigerant Substances 0.000 abstract description 4
- 230000002093 peripheral effect Effects 0.000 abstract description 3
- 230000007423 decrease Effects 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000009795 derivation Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Landscapes
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【発明の詳細な説明】 （イ）産業上の利用分野 この発明は回転圧縮機の回転軸に関する。[Detailed description of the invention] (b) Industrial application field The present invention relates to a rotating shaft of a rotary compressor.
（ロ）従来の技術
従来の回転圧縮機は例えば実公昭６１−２０３１７号公
報に示されているように構成されている。ここで、この
公報を参考に従来例を説明する。第４図において、５ｏ
は密閉容器で、この容器内の下部に位置する回転圧縮要
素５１はその上部の電動要素５２より回転軸５３を介し
て駆動されるようになっている。そして、この駆動によ
り吸入ガスは吸入管５４を経て、シリンダ５５内に吸入
され、回転軸５３のクランク部５６に嵌合ゎきれたロー
ラ５７の偏心回転によって圧縮きれて密閉容器５０内に
吐出され、この容器内は吐出ガスによって高温高圧とな
る。また、回転圧縮要素５１は密閉容器５ｏ内のオイル
に浸されており、一方このオイルは油キャップ５８によ
り回転軸５３の内部の給油孔５９へ吸上げられて回転圧
縮要素５１の各摺動面に供給される。尚、シリンダ５５
の両端面は上軸受６ｏ、下軸受６１で気密に封じられて
いる。クランク部５６の下部には下軸受６１に接触する
スラスト面６２が設けられている。ローラ５７の上下端
面には上軸受６０と下軸受６１との間でクリアランスが
設けられている。(B) Prior Art A conventional rotary compressor is constructed as shown in, for example, Japanese Utility Model Publication No. 61-20317. Here, a conventional example will be explained with reference to this publication. In Figure 4, 5o
is a closed container, and a rotary compression element 51 located at the lower part of the container is driven by an electric element 52 at the upper part via a rotating shaft 53. As a result of this drive, suction gas is sucked into the cylinder 55 through the suction pipe 54, compressed by the eccentric rotation of the roller 57 that is fully fitted into the crank portion 56 of the rotating shaft 53, and then discharged into the sealed container 50. The inside of this container becomes high temperature and high pressure due to the discharged gas. Further, the rotary compression element 51 is immersed in oil in the closed container 5o, and on the other hand, this oil is sucked up by the oil cap 58 into the oil supply hole 59 inside the rotary shaft 53, and the oil is sucked up to each sliding surface of the rotary compression element 51. supplied to Furthermore, the cylinder 55
Both end surfaces of are hermetically sealed with an upper bearing 6o and a lower bearing 61. A thrust surface 62 that contacts the lower bearing 61 is provided at the lower part of the crank portion 56 . A clearance is provided between an upper bearing 60 and a lower bearing 61 on the upper and lower end surfaces of the roller 57.
回転軸５３には回転圧縮要素５１の各摺動面にオイルを
供給する導出孔６３が給油孔５９に連通して設けられて
いる。The rotary shaft 53 is provided with a derivation hole 63 communicating with the oil supply hole 59 for supplying oil to each sliding surface of the rotary compression element 51 .
この構造の回転圧縮機では油キャップ５８から給油孔５
９へ汲上げられたオイルをクランク部５６に設けられた
導出孔６３からローラ５７の内部に供給し、この内部に
溜ったオイルをローラ５７の上下端面に設けられたクリ
アランスからシリンダ５５内に供給し、このシリンダ内
のシール性と耐摩耗性とが向上するようにしている。In a rotary compressor with this structure, the oil supply hole 5 is connected to the oil cap 58.
The oil pumped up into the roller 9 is supplied to the inside of the roller 57 from the outlet hole 63 provided in the crank part 56, and the oil accumulated inside this is supplied to the inside of the cylinder 55 from clearances provided on the upper and lower end surfaces of the roller 57. However, the sealing performance and wear resistance inside this cylinder are improved.
（ハ）発明が解決しようとする課題
しかしながら、従来の回転軸５３は上軸受６０及び下軸
受６１で軸支される軸の直径が同じであるとともに、下
軸受６１の接触するスラスト面６２を大きく形成してい
るため、軸受での周速が速くオイル供給が十分に行われ
ていないと摩擦抵抗が大きくなるとともに、スラスト面
６２の接触面積が大きくなって摩擦抵抗が大きくなり、
回転圧縮機の機械効率が低下する問題があった。(C) Problems to be Solved by the Invention However, in the conventional rotary shaft 53, the diameters of the shafts supported by the upper bearing 60 and the lower bearing 61 are the same, and the thrust surface 62 in contact with the lower bearing 61 is made larger. Because of this, if the circumferential speed of the bearing is high and the oil supply is not sufficient, the frictional resistance will increase, and the contact area of the thrust surface 62 will increase, resulting in increased frictional resistance.
There was a problem that the mechanical efficiency of the rotary compressor decreased.
この発明は上記の問題を解決するもので、回転軸の周速
を減少させるとともに、スラスト荷重による摩擦抵抗を
減少させる圧縮機の回転軸を提供することを目的とした
ものである。This invention solves the above problems, and aims to provide a rotating shaft for a compressor that reduces the peripheral speed of the rotating shaft and reduces the frictional resistance due to thrust loads.
（ニ）課題を解決するための手段
この発明は密閉容器内にクランク部を有する回転軸と、
この回転軸で連結された電動要素及び回転圧縮要素とを
収納し、前記回転圧縮要素を、シリンダと、このシリン
ダ内で回転軸のクランク部に嵌合わされたローラと、こ
のローラに接してシフンダ内を高圧室及び低圧室に区画
するベーンと、前記シリンダの両開口を封じるとともに
、回転軸をクランク部の両側で軸支する上軸受及び下軸
受とで構成し、前記クランク部に下軸受に接触するスラ
スト部を設けた回転圧縮機において、前記上軸受側で軸
支される回転軸の直径Ｄ３を下軸受側で軸支される回転
軸の直径Ｄ２より軸径を細くするとともに、スラスト部
の直径Ｄ３を直径り。(d) Means for Solving the Problems This invention provides a rotating shaft having a crank portion inside a closed container;
An electric element and a rotary compression element connected by the rotating shaft are housed, and the rotary compression element is connected to a cylinder, a roller fitted to the crank part of the rotating shaft within the cylinder, and a sifunder in contact with the roller. a vane that divides the cylinder into a high-pressure chamber and a low-pressure chamber, and an upper bearing and a lower bearing that seal both openings of the cylinder and pivotally support the rotating shaft on both sides of the crank part, and the lower bearing contacts the crank part. In a rotary compressor equipped with a thrust section, the diameter D3 of the rotating shaft supported on the upper bearing side is made smaller than the diameter D2 of the rotating shaft supported on the lower bearing side, and Measure the diameter D3.
の回転軸の１．３倍以下に設定したものである。The rotation axis is set to 1.3 times or less.
（＊）作用
この発明は上記のように構成したことにより、下軸受側
の回転軸を上軸受側の回転軸より細くするとともに、ス
ラスト部の直径を下軸受側の回転軸の直径の１．３倍以
下にし、回転軸に必要な強度を落とすことなく周速を遅
くして摩擦抵抗を減マ之
少隼るとともに、スラスト面の摩擦抵抗を減少させて圧
縮機の機械効率を向上させられるようにしたものである
。(*) Effect By having the present invention configured as described above, the rotating shaft on the lower bearing side is made thinner than the rotating shaft on the upper bearing side, and the diameter of the thrust portion is set to 1.5 times the diameter of the rotating shaft on the lower bearing side. By reducing the friction resistance to less than 3 times, it is possible to reduce the circumferential speed and reduce frictional resistance without reducing the strength required for the rotating shaft, and to improve the mechanical efficiency of the compressor by reducing the frictional resistance on the thrust surface. This is how it was done.
（へ）実施例
以下この発明を第１図及び第２図に示す実施例に基いて
説明する。(f) Examples The present invention will be explained below based on the examples shown in FIGS. 1 and 2.
１は密閉容器で、この容器内には中央に回転軸２と、こ
の回転軸の上部に取付けた電動要素３と、回転軸２の下
部に取付けた回転圧縮要素４とが収納されている。電動
要素３は固定子５と、この固定子の内部で回転軸２に装
着された回転子６とで形成されている。回転圧縮要素４
はシリンダ７と、回転軸２のクランク部８によってシリ
ンダ７内を回転するローラ９と、このローラに接してシ
リンダ７内を高圧室及び低圧室に区画するベーン１０と
、シリンダ７の両開口を封じる上軸受１１及び下軸受１
２と、この上軸受に設けられた吐出弁１３を覆うように
取付けたカップマフラ１４とで構成されている。Reference numeral 1 denotes a closed container, and this container houses a rotating shaft 2 in the center, an electric element 3 attached to the upper part of the rotating shaft, and a rotary compression element 4 attached to the lower part of the rotating shaft 2. The electric element 3 is formed by a stator 5 and a rotor 6 mounted on the rotating shaft 2 inside the stator. Rotary compression element 4
consists of a cylinder 7, a roller 9 that rotates inside the cylinder 7 by the crank part 8 of the rotating shaft 2, a vane 10 that contacts this roller and divides the inside of the cylinder 7 into a high pressure chamber and a low pressure chamber, and both openings of the cylinder 7. Upper bearing 11 and lower bearing 1 to be sealed
2, and a cup muffler 14 attached to cover the discharge valve 13 provided on the upper bearing.
回転軸２はクランク部８の上方で回転子６に装着きれる
とともに、上軸受１１で軸支される直径Ｄ１の長軸１５
と、クランク部８の下方で下軸受１２によって軸支され
る直径Ｄ２の短軸１６とで形成され、この短軸を長軸１
５の直径より細くしている。また、回転軸２のクランク
部８の下端には下軸受１２に接触するスラスト部１７が
設けられている。このスラスト面の直径Ｄ３は短軸１６
の直径Ｄ２の１．３倍以下に設定されている。The rotating shaft 2 can be attached to the rotor 6 above the crank part 8, and a long shaft 15 with a diameter D1 is supported by an upper bearing 11.
and a short shaft 16 with a diameter D2 which is supported by a lower bearing 12 below the crank part 8, and this short shaft is connected to the long axis 1.
It is thinner than the diameter of 5. Further, a thrust portion 17 that contacts the lower bearing 12 is provided at the lower end of the crank portion 8 of the rotating shaft 2 . The diameter D3 of this thrust surface is the short axis 16
The diameter D2 is set to 1.3 times or less.
１８は密閉容器１の上部に設けられた吐出管である。18 is a discharge pipe provided at the upper part of the closed container 1.
このように構成された回転圧縮機の回転軸において、シ
リンダ７内に流入した冷媒はローラ９とベーン１０との
協働によって圧縮され、吐出弁１３を開放してカップマ
フラ１４内に吐出される。In the rotating shaft of the rotary compressor configured in this manner, the refrigerant flowing into the cylinder 7 is compressed by the cooperation of the rollers 9 and vanes 10, and is discharged into the cup muffler 14 by opening the discharge valve 13. .
このカップマフラ内の冷媒は密閉容器１内に吐出され、
電動要素３を通って吐出管１８から密閉容器１外に吐出
される。The refrigerant in this cup muffler is discharged into the sealed container 1,
It passes through the electric element 3 and is discharged from the discharge pipe 18 to the outside of the closed container 1 .
回転軸２は短軸１６の直径Ｄ３を長軸１５の直径Ｄ２よ
り細くすることにより、下軸受１２との相対的な周速を
下げることができ、摩擦抵抗を減少させて圧縮機の機械
効率を向上させられるとともに、回転子６を装着して上
軸受１１に軸支される長軸１５の強度が損なわれないよ
うにし、軸のたわみや起動時の吸引等による固定子５と
回転子６との当りの発生を抑えられるようにしている。By making the diameter D3 of the short shaft 16 of the rotating shaft 2 smaller than the diameter D2 of the long shaft 15, the peripheral speed relative to the lower bearing 12 can be lowered, reducing frictional resistance and improving the mechanical efficiency of the compressor. At the same time, the strength of the long shaft 15 supported by the upper bearing 11 is not impaired by attaching the rotor 6, and the stator 5 and rotor 6 are prevented from being damaged due to shaft deflection or suction during startup. This is to prevent the occurrence of collisions.
また、回転軸２のクランク部８のスラスト面１７は短軸
１６の直径の１．３倍以下の直径にすることにより、回
転子６の重量と回転軸２の重量とによるスラスト荷重を
受ける下軸受１２との間の接触面積が／ＪＸさくなり、
摩擦抵抗の増加を抑えられるようにしている。Furthermore, by making the thrust surface 17 of the crank part 8 of the rotating shaft 2 have a diameter that is 1.3 times or less than the diameter of the short shaft 16, the thrust surface 17 can receive the thrust load due to the weight of the rotor 6 and the weight of the rotating shaft 2. The contact area with the bearing 12 is /JX smaller,
This makes it possible to suppress an increase in frictional resistance.
このことは、第３図に示す実験結果から確認された。す
なわち、スラスト径り、／短軸径Ｄ２の比をこの発明の
回転軸２では１．２１、従来の回転軸では１．５８とし
、異なる冷凍能力の回転圧縮機で実験を行っても同様な
傾向が見られた。このことから、回転軸２は短軸１６を
細くするとともに、スラスト面１７の接触面積を小さく
することにより、摩擦抵抗の減少から冷凍能力比の向上
を図ることができるものである。This was confirmed from the experimental results shown in FIG. That is, the ratio of thrust radius/minor axis diameter D2 was set to 1.21 for the rotating shaft 2 of the present invention and 1.58 for the conventional rotating shaft, and the same results were obtained even when experiments were conducted using rotary compressors with different refrigerating capacities. A trend was observed. Therefore, by making the short axis 16 of the rotating shaft 2 thinner and reducing the contact area of the thrust surface 17, it is possible to improve the refrigerating capacity ratio by reducing the frictional resistance.
この発明は回転軸２の短軸１６を長軸１５の軸径より細
くするとともに、スラスト面１７の直径を短軸１６の直
径の１．３倍以下にすることにより、回転軸２の周速を
部分的に遅くするとともに、スラスト面１７の接触面積
を小さくして摩擦抵抗の減少を図り冷凍能力比を向上さ
せたものである。This invention makes the short axis 16 of the rotating shaft 2 thinner than the diameter of the long axis 15, and also makes the diameter of the thrust surface 17 1.3 times or less the diameter of the short shaft 16, thereby increasing the circumferential speed of the rotating shaft 2. The cooling capacity ratio is improved by partially slowing down the flow rate and by reducing the contact area of the thrust surface 17 to reduce frictional resistance.
（ト）発明の効果
以上のようにこの発明によれば、上軸受側で軸支きれる
回転軸の直径Ｄ３を下軸受側で軸支される回転軸の直径
Ｄ２より軸径を細くするとともに、スラスト部の直径Ｄ
３を直径Ｄ２の回転軸の１．３倍以下に設定したもので
あるから、回転軸の強度を低下させることなく、前記回
転軸の回転による摩擦抵抗を減少でき、かつ、スラスト
部のスラスト荷重による摩擦抵抗を低減でき、圧縮機の
冷凍能力比を向上できるようにしたものである。(G) Effects of the Invention As described above, according to the present invention, the diameter D3 of the rotating shaft supported on the upper bearing side is made smaller than the diameter D2 of the rotating shaft supported on the lower bearing side, and Thrust diameter D
3 is set to 1.3 times or less of the rotating shaft having a diameter D2, the frictional resistance caused by the rotation of the rotating shaft can be reduced without reducing the strength of the rotating shaft, and the thrust load on the thrust part can be reduced. It is possible to reduce the frictional resistance caused by the compressor and improve the refrigerating capacity ratio of the compressor.
第１図はこの発明の一実施例を示す回転圧縮機の縦断面
図、第２図は同じく回転軸の正面図、第３図は回転圧縮
機の冷凍能力比を示す特性図、第４図は従来の回転圧縮
機の縦断面図である。
１・・・密閉容器、 ２・・・回転軸、 ３・・・電
動要素、 ４・・・回転圧縮要素、 ７・・・シリ
ンダ、 ８・・・クランク部、 ９・・・ローラ、
１０・・・ベーン、１１・・・上軸受、 １２・
・・下軸受、 １７・・・スラスト部。
第１！！１Fig. 1 is a longitudinal sectional view of a rotary compressor showing an embodiment of the present invention, Fig. 2 is a front view of the rotating shaft, Fig. 3 is a characteristic diagram showing the refrigerating capacity ratio of the rotary compressor, and Fig. 4 is a longitudinal sectional view of a conventional rotary compressor. DESCRIPTION OF SYMBOLS 1... Airtight container, 2... Rotating shaft, 3... Electric element, 4... Rotating compression element, 7... Cylinder, 8... Crank part, 9... Roller,
10... Vane, 11... Upper bearing, 12.
...Lower bearing, 17...Thrust part. 1st! ! 1
Claims (1)
転軸で連結された電動要素及び回転圧縮要素とを収納し
、前記回転圧縮要素を、シリンダと、このシリンダ内で
回転軸のクランク部に嵌合わされたローラと、このロー
ラに接してシリンダ内を高圧室及び低圧室に区画するベ
ーンと、前記シリンダの両開口を封じるとともに、回転
軸をクランク部の両側で軸支する上軸受及び下軸受とで
構成し、前記クランク部に下軸受に接触するスラスト部
を設けた回転圧縮機において、前記上軸受側で軸支され
る回転軸の直径Ｄ＿１を下軸受側で軸支される回転軸の
直径Ｄ＿２より軸径を細くするとともに、スラスト部の
直径Ｄ＿３を直径Ｄ＿２の回転軸の１．３倍以下に設定
したことを特徴とする回転圧縮機の回転軸。1. A rotary shaft having a crank part, and an electric element and a rotary compression element connected by this rotary shaft are housed in a sealed container, and the rotary compression element is connected to a cylinder and a crank part of the rotary shaft within the cylinder. a roller fitted to the cylinder, a vane that contacts the roller and divides the inside of the cylinder into a high pressure chamber and a low pressure chamber, and an upper and lower bearing that seals both openings of the cylinder and pivotally supports the rotating shaft on both sides of the crank section. In a rotary compressor in which the crank part is provided with a thrust part that contacts the lower bearing, the diameter D_1 of the rotating shaft supported on the upper bearing side is equal to the diameter D_1 of the rotating shaft supported on the lower bearing side. A rotating shaft of a rotary compressor, characterized in that the shaft diameter is smaller than the diameter D_2 of the rotary compressor, and the diameter D_3 of the thrust part is set to 1.3 times or less of the rotating shaft having a diameter D_2.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14957790A JPH0441989A (en) | 1990-06-07 | 1990-06-07 | Rotation shaft for rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14957790A JPH0441989A (en) | 1990-06-07 | 1990-06-07 | Rotation shaft for rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0441989A true JPH0441989A (en) | 1992-02-12 |
Family
ID=15478239
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP14957790A Pending JPH0441989A (en) | 1990-06-07 | 1990-06-07 | Rotation shaft for rotary compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0441989A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2017002793A (en) * | 2015-06-09 | 2017-01-05 | パナソニック株式会社 | Liquid pump and Rankine cycle device |
-
1990
- 1990-06-07 JP JP14957790A patent/JPH0441989A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2017002793A (en) * | 2015-06-09 | 2017-01-05 | パナソニック株式会社 | Liquid pump and Rankine cycle device |
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