JPS6118232Y2 - - Google Patents
Info
- Publication number
- JPS6118232Y2 JPS6118232Y2 JP1977103131U JP10313177U JPS6118232Y2 JP S6118232 Y2 JPS6118232 Y2 JP S6118232Y2 JP 1977103131 U JP1977103131 U JP 1977103131U JP 10313177 U JP10313177 U JP 10313177U JP S6118232 Y2 JPS6118232 Y2 JP S6118232Y2
- Authority
- JP
- Japan
- Prior art keywords
- rotor
- hole
- rotary compressor
- recess
- end surface
- 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.)
- Expired
Links
- 230000006835 compression Effects 0.000 claims description 9
- 238000007906 compression Methods 0.000 claims description 9
- 238000013459 approach Methods 0.000 claims description 2
- 230000002093 peripheral effect Effects 0.000 claims 1
- 239000003921 oil Substances 0.000 description 20
- 239000010687 lubricating oil Substances 0.000 description 12
- 238000005461 lubrication Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 1
- 238000005553 drilling Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 230000001052 transient effect Effects 0.000 description 1
Description
【考案の詳細な説明】
この考案は、回転式圧縮機に関し、とくにその
駆動用電動機の回転子に付加される釣合重錘を省
略して回転子の製作工程を簡易化し、圧縮機の重
量を軽減すると共に、起動時における摺動部分へ
の潤滑油の供給を良好にした回転式圧縮機に関す
るものである。[Detailed description of the invention] This invention relates to a rotary compressor, and in particular, it simplifies the manufacturing process of the rotor by omitting the counterweight added to the rotor of the driving electric motor, thereby reducing the weight of the compressor. The present invention relates to a rotary compressor that reduces friction and improves the supply of lubricating oil to sliding parts during startup.
第１図、第２図は従来の回転式圧縮機の一例を
示す。これらの図において、１は圧縮機の電動要
素Ａおよび圧縮要素Ｂを収容する密閉容器であ
る。圧縮要素Ｂのシリンダ２内には楕円回転子３
が嵌装され、この回転子３の長径部外周面がシリ
ンダ２の内周面に摺接し、ベーン４がこれらの背
部にあるばね５により楕円回転子３の外周面に圧
接され、シリンダ２内を圧縮室６と吸入室７とに
分離している。圧縮要素Ｂを駆動する電動要素Ａ
は、固定子８と回転子９とからなり、この回転子
９は軸１０を介して楕円回転子３を第２図の反時
計方向に回転させ、吸入口１１から被圧縮気体を
シリンダ２内に吸込んべ圧縮し、圧縮した気体を
吐出孔１２から吐出弁１３を経て密閉容器内空間
１４に吐出した後、吐出管１５から外部に導く。
密閉容器１の底部に位置する潤滑油１６は、軸１
０の偏心給油孔１７によつて各摺動部へ供給され
るが、給油量の調整と潤滑油の逃がしのために、
楕円回転子３に油溜り部１８と連通孔１９とが設
けられ、また、フレーム２０内には排油孔２１が
穿たれている。なお、第１図中、２２はシリンダ
ヘツドである。 1 and 2 show an example of a conventional rotary compressor. In these figures, 1 is a closed container that houses an electric element A and a compression element B of the compressor. Inside the cylinder 2 of the compression element B is an elliptical rotor 3.
is fitted, the outer circumferential surface of the long diameter part of this rotor 3 is in sliding contact with the inner circumferential surface of the cylinder 2, and the vanes 4 are pressed against the outer circumferential surface of the elliptical rotor 3 by the spring 5 on the back of these vanes, and the inner circumferential surface of the elliptical rotor 3 is separated into a compression chamber 6 and a suction chamber 7. Electric element A that drives compression element B
consists of a stator 8 and a rotor 9, and the rotor 9 rotates the elliptical rotor 3 counterclockwise in FIG. The compressed gas is discharged from the discharge hole 12 through the discharge valve 13 into the internal space 14 of the closed container, and then guided to the outside through the discharge pipe 15.
The lubricating oil 16 located at the bottom of the closed container 1 is
The lubricating oil is supplied to each sliding part through the eccentric lubricating hole 17, but in order to adjust the amount of lubricating oil and to release the lubricating oil,
An oil reservoir 18 and a communication hole 19 are provided in the elliptical rotor 3, and an oil drain hole 21 is bored in the frame 20. In addition, in FIG. 1, 22 is a cylinder head.
前述した楕円回転子を備えた従来の回転式圧縮
機は、すべて部品が軸１０の中心に対して点対称
になつているが、偏心給油孔１７を設けているた
めに回転系に不釣合が生じ、釣合重錘２３，２４
を電動要素の回転子９に設けることが必要とな
る。このため、回転子９の製作工程が煩雑になる
だけではなく、圧縮機の重量を増大させる。ま
た、偏心給油孔１７は、軸１０の回転が定常運転
に達した場合には十分な油量の潤滑油を供給でき
るが、起動直後の低速回転中は給油量が十分では
なく、とくに電動要素が単相用の電動機の場合に
は給油量が不十分になる傾向が強い。 In the conventional rotary compressor equipped with the elliptical rotor mentioned above, all the parts are point symmetrical with respect to the center of the shaft 10, but since the eccentric oil supply hole 17 is provided, an imbalance occurs in the rotating system. , counterweights 23, 24
It is necessary to provide the rotor 9 of the electric element. This not only complicates the manufacturing process of the rotor 9 but also increases the weight of the compressor. In addition, the eccentric oil supply hole 17 can supply a sufficient amount of lubricating oil when the rotation of the shaft 10 reaches steady operation, but the amount of oil supplied is not sufficient during low-speed rotation immediately after startup, especially when the electric element However, in the case of a single-phase electric motor, there is a strong tendency for the amount of oil to be insufficient.
この考案は、前述した両欠点を解消するために
なされたもので、電動要素の回転子の釣合重錘を
不要にし、また、起動と同時に回転子の上端面の
摺動文への潤滑油の十分な供給を可能にするもの
である。 This idea was made to solve both of the above-mentioned drawbacks, and it eliminates the need for a counterbalance weight for the rotor of the electric element, and also allows lubricating oil to be applied to the sliding ring on the upper end of the rotor at the same time as startup. This will enable an adequate supply of
以下この考案の実施例を図面に基いて説明す
る。 Examples of this invention will be described below with reference to the drawings.
第３図は楕円回転子３（楕円近似形状の回転子
を含む）部を示し、この実施例では楕円回転子３
の油溜り部１８を含む上、下端面の平面部に穿孔
することにより、軸１０に形成した偏心給油孔１
７によつて生ずる不釣合量を打消したものであ
る。すなわち、偏心給油孔１７の偏心側の釣合孔
２５は楕円回転子３の下端面の油溜り部１８の段
違い平面に穿設した小径で深さの短い不透孔であ
り、偏心給油孔１７の偏心と反対側の釣合孔２６
は楕円回転子３上端面のフレーム（図示せず）と
の摺動面に穿設した大径で深さが長い不透孔であ
る。 FIG. 3 shows the elliptical rotor 3 (including a rotor with an approximate shape of an ellipse), and in this embodiment, the elliptic rotor 3
An eccentric oil supply hole 1 is formed in the shaft 10 by drilling in the flat parts of the upper and lower end faces including the oil reservoir part 18.
This cancels the unbalance caused by 7. That is, the balancing hole 25 on the eccentric side of the eccentric oil supply hole 17 is an impermeable hole with a small diameter and short depth, which is bored in the stepped plane of the oil reservoir portion 18 on the lower end surface of the elliptical rotor 3. The counterbalancing hole 26 on the opposite side to the eccentricity of
is an impermeable hole with a large diameter and a long depth, which is bored in the upper end surface of the elliptical rotor 3 on the sliding surface with the frame (not shown).
第３図(a)は、回転系に対するバランスを示した
ものであり、w1r1は偏心給油孔１７の不釣合量、
w2r2は釣合孔２６のアンバランス量、w3r3は釣合
孔２５のアンバランス量に対応する。そして、
下式 w1r1＋w3r3＝w2r2
w2r2×ｌ＝w3r3×Ｌ
を満足させるように釣合孔２５，２６の位置内径
および深さを決定することにより、回転系の静お
よび動釣合がともにとれることになり、電動要素
の釣合重錘が不要となる。 Figure 3(a) shows the balance for the rotating system, where w 1 r 1 is the unbalance amount of the eccentric oil supply hole 17,
w 2 r 2 corresponds to the unbalance amount of the balancing hole 26, and w 3 r 3 corresponds to the unbalance amount of the balancing hole 25. Then, determine the inner diameter and depth of the balancing holes 25 and 26 so as to satisfy the following formula: w 1 r 1 + w 3 r 3 = w 2 r 2 w 2 r 2 ×l = w 3 r 3 ×L As a result, both the static and dynamic balance of the rotating system can be maintained, and a balancing weight for the electric element is not required.
第４図は、楕円回転子３の上端面の油溜り部１
８に釣合孔２６を穿設した他例を示し、この釣合
孔２６は、偏心給油孔の偏心と反対側に軸１０の
中心線に対して軸線を傾斜させて形成し、釣合孔
２６の開口面がその底部より軸１０の中心線に対
して離れるようにしてある。このため、圧縮機の
運転中には遠心力のため、釣合孔２６に潤滑油が
溜ることがない。しかし、圧縮機が停止すると油
溜り部１８内にあつた潤滑油の一部が釣合孔２６
を満たす。次の起動時に、釣合孔２６内の潤滑油
が遠心力によつて半径方向に飛散し、楕円回転子
３とフレームとの摺動面を良好な潤滑状態に保
ち、回転数が上昇して偏心給油孔１７から十分な
給油が行なわれるまでの過渡的な潤滑不足を解消
する。 FIG. 4 shows the oil reservoir 1 on the upper end surface of the elliptical rotor 3.
8 shows another example in which a balancing hole 26 is bored. The opening surface of 26 is arranged to be farther away from the centerline of shaft 10 than the bottom thereof. Therefore, during operation of the compressor, lubricating oil does not accumulate in the balancing hole 26 due to centrifugal force. However, when the compressor stops, some of the lubricating oil in the oil reservoir 18 is absorbed into the balancing hole 26.
satisfy. At the next startup, the lubricating oil in the balancing hole 26 is scattered in the radial direction by centrifugal force, keeping the sliding surfaces between the elliptical rotor 3 and the frame in a good lubricated state, and the rotation speed increases. To solve a transient lack of lubrication until sufficient oil is supplied from an eccentric oil supply hole 17.
第５図は楕円回転子３の上端面の油溜り部１８
に釣合孔２６に代えて窪み２７を設け、この窪み
２７を平面扇形とし、この扇形の円弧部分をかな
め部分よりも回転子３の外周側に位置させると共
に、窪み２７の深さをかなめ部分を深く、円弧部
分に近づくに従つて浅くなるようにしたものであ
る。従つて圧縮機の停止中、前記窪み２７に溜つ
ていた潤滑油は、次の起動時に遠心力によつて飛
散し、第４図の場合と同様な効果が期待できる。 FIG. 5 shows an oil reservoir 18 on the upper end surface of the elliptical rotor 3.
A recess 27 is provided in place of the balancing hole 26, and the recess 27 is made into a fan shape in plan view, and the arc portion of the fan shape is positioned closer to the outer circumference of the rotor 3 than the latch portion, and the depth of the recess 27 is set to the latch portion. is deep, and becomes shallower as it approaches the arc. Therefore, the lubricating oil accumulated in the recess 27 while the compressor is stopped will be scattered by the centrifugal force when the compressor is next started, and the same effect as in the case of FIG. 4 can be expected.
なお、第４図、第５図のものに比べて劣るが第
３図の釣合孔２６でも、前述した圧縮機の起動時
における潤滑効果を期待できる。 Although the balancing hole 26 shown in FIG. 3 is inferior to that shown in FIGS. 4 and 5, it can be expected that the above-mentioned lubrication effect at the time of starting the compressor can be expected.
また、この考案において前述した以外の構成お
よび動作は、電動要素に釣合重錘を設けないだけ
で、第１図、第２図の従来の圧縮機と同様である
から説明を省略する。 In addition, the configuration and operation of this invention other than those described above are the same as those of the conventional compressor shown in FIGS. 1 and 2, except that the electric element is not provided with a counterweight, and therefore the explanation thereof will be omitted.
以上説明したようにこの考案の回転式圧縮機に
よれば、電動要素の回転子の釣合重錘が不要にな
るので回転子の製作が容易となり、偏心給油孔１
７との釣合を圧縮要素の回転子３の釣合孔２６、
窪み２７によつて実現させるものであるから、圧
縮機重量の軽減が可能である。さらに、前記孔２
６、窪み２７により、圧縮機の起動直後における
回転子３とフレーム２０との潤滑状態を良好に保
ち、焼付きを防止でき、とくに第４図、第５図の
ものでは効果的である。 As explained above, according to the rotary compressor of this invention, the balancing weight of the rotor of the electric element is not required, so the rotor can be manufactured easily, and the eccentric oil supply hole 1
7 and the balance hole 26 of the rotor 3 of the compression element,
Since this is realized by the recess 27, the weight of the compressor can be reduced. Furthermore, the hole 2
6. The recesses 27 can maintain a good lubrication state between the rotor 3 and the frame 20 immediately after the compressor is started, and prevent seizure, which is particularly effective in the configurations shown in FIGS. 4 and 5.
第１図は従来の回転式圧縮機の一例を示す縦断
面図、第２図は同圧縮要素部分の横断面図、第３
図はこの考案の一実施例を示す楕円回転子部分の
縦断面図、第３図(a)は前記実施例の作用説明図、
第４図はこの考案の他の実施例を示す楕円回転子
の縦断面図、第５図はこの考案のさらに他の実施
例を示す楕円回転子の一部切欠き斜視図である。
Ａ……電動要素、Ｂ……圧縮要素、１……密閉
容器、２……シリンダ、３……楕円回転子、４…
…ベーン、５……ばね、６……圧縮室、７……吸
入室、８……固定子、９……電動要素の回転子、
１０……軸、１１……吸入孔、１２……吐出孔、
１３……吐出弁、１４……密閉容器内空間、１５
……吐出管、１６……潤滑油、１７……偏心給油
孔、１８……油溜り部、１９……連通孔、２０…
…フレーム、２１……排油孔、２２……シリンダ
ヘツド、２３，２４……釣合重錘、２５，２６…
…釣合孔、２７……窪み。なお、図中同一符号は
同一または相当部分を示す。
Figure 1 is a vertical cross-sectional view showing an example of a conventional rotary compressor, Figure 2 is a cross-sectional view of the compression element, and Figure 3 is a cross-sectional view of an example of a conventional rotary compressor.
The figure is a longitudinal sectional view of an elliptical rotor portion showing an embodiment of this invention, and FIG. 3(a) is an explanatory diagram of the operation of the embodiment.
FIG. 4 is a longitudinal cross-sectional view of an elliptical rotor showing another embodiment of this invention, and FIG. 5 is a partially cutaway perspective view of an elliptical rotor showing still another embodiment of this invention. A... Electric element, B... Compression element, 1... Closed container, 2... Cylinder, 3... Elliptical rotor, 4...
... Vane, 5 ... Spring, 6 ... Compression chamber, 7 ... Suction chamber, 8 ... Stator, 9 ... Rotator of electric element,
10... shaft, 11... suction hole, 12... discharge hole,
13...Discharge valve, 14...Inner space of sealed container, 15
...Discharge pipe, 16...Lubricating oil, 17...Eccentric oil supply hole, 18...Oil reservoir, 19...Communication hole, 20...
... Frame, 21 ... Oil drain hole, 22 ... Cylinder head, 23, 24 ... Counterweight, 25, 26 ...
...Balancing hole, 27... recess. Note that the same reference numerals in the figures indicate the same or corresponding parts.
Claims (1)
転する回転子３と、この回転子３の外周面に接
して往復運動するベーン４とにより、前記シリ
ンダ２内を吸入室７と圧縮室６とに分けるよう
にした回転式圧縮機において、前記回転子３の
上端面に対向面までは貫通しない孔２６または
窪み２７の少なくとも一方を回転系の釣合をと
るために前記回転軸１０の軸線を含む不釣合い
面内に設けたことを特徴とする回転式圧縮機。 (2) 回転子３の上端面に設けた孔２６の軸線を回
転子３の軸１０の中心線に対して傾斜させ、孔
２６の開口面がその底面より軸１０の中心線に
対して離れるようにしたことを特徴とする実用
新案登録請求の範囲第１項記載の回転式圧縮
機。 (3) 回転子３の上端面に設けた窪み２７を平面扇
形とし、この扇形の円弧部分をかなめ部分より
も回転子３の外周側に位置させると共に、窪み
２７の深さをかなめ部分が深く円弧部分に近づ
くに従つて浅くなるようにしたことを特徴とす
る回転式圧縮機。[Claims for Utility Model Registration] (1) A rotor 3 that rotates integrally with the rotating shaft 10 inside the cylinder 2, and a vane 4 that reciprocates in contact with the outer peripheral surface of the rotor 3, In a rotary compressor in which the inside of the rotor 3 is divided into a suction chamber 7 and a compression chamber 6, at least one of a hole 26 or a recess 27 that does not penetrate to the opposite surface on the upper end surface of the rotor 3 is used to balance the rotating system. A rotary compressor characterized in that the rotary compressor is provided within an unbalanced plane that includes the axis of the rotating shaft 10 in order to take the above-mentioned. (2) The axis of the hole 26 provided in the upper end surface of the rotor 3 is inclined with respect to the center line of the shaft 10 of the rotor 3, and the opening surface of the hole 26 is separated from the center line of the shaft 10 from the bottom surface thereof. A rotary compressor according to claim 1 of the utility model registration, characterized in that: (3) The recess 27 provided on the upper end surface of the rotor 3 has a planar fan shape, and the arc portion of this fan shape is located closer to the outer circumference of the rotor 3 than the latch, and the depth of the recess 27 is set so that the latch is deeper. A rotary compressor characterized in that it becomes shallower as it approaches an arcuate portion.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1977103131U JPS6118232Y2 (en) | 1977-08-01 | 1977-08-01 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1977103131U JPS6118232Y2 (en) | 1977-08-01 | 1977-08-01 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5429405U JPS5429405U (en) | 1979-02-26 |
| JPS6118232Y2 true JPS6118232Y2 (en) | 1986-06-03 |
Family
ID=29043357
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1977103131U Expired JPS6118232Y2 (en) | 1977-08-01 | 1977-08-01 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6118232Y2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58217791A (en) * | 1982-06-09 | 1983-12-17 | Matsushita Refrig Co | Rotary compressor |
| JP2536766Y2 (en) * | 1990-03-06 | 1997-05-28 | 株式会社城南製作所 | Emergency mechanism of power transmission |
-
1977
- 1977-08-01 JP JP1977103131U patent/JPS6118232Y2/ja not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5429405U (en) | 1979-02-26 |
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