JPH0758076B2 - Rotary compressor - Google Patents
Rotary compressorInfo
- Publication number
- JPH0758076B2 JPH0758076B2 JP406888A JP406888A JPH0758076B2 JP H0758076 B2 JPH0758076 B2 JP H0758076B2 JP 406888 A JP406888 A JP 406888A JP 406888 A JP406888 A JP 406888A JP H0758076 B2 JPH0758076 B2 JP H0758076B2
- Authority
- JP
- Japan
- Prior art keywords
- discharge muffler
- discharge
- refrigerant gas
- discharge port
- rotary compressor
- 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 - Lifetime
Links
Landscapes
- Applications Or Details Of Rotary Compressors (AREA)
Description
この発明は、主として冷凍、空気調和用に用いられ、冷
媒ガスを圧縮する回転型圧縮機に関するものである。The present invention relates to a rotary compressor that is mainly used for refrigeration and air conditioning and that compresses a refrigerant gas.
第５図は例えば実開昭60−3351号公報に示された従来の
回転型圧縮機の縦断面図である。第３図において、１は
密閉容器、２は密閉容器１内に支持固定された電動機、
３は電動機２の回転軸、４は電動機２の駆動により回転
軸３によって駆動される圧縮機構であり、圧縮機構４は
次の各部を備えている。５は密閉容器１内に支持固定さ
れたシリンダ、６は回転軸３に取り付けられたローリン
グピストン、７は上部軸受、８は下部軸受であり、上，
下軸受7,8は回転軸３を軸支している。９は下軸受８に
設けられた吐出ポート、10は下軸受８の外周面に圧入さ
れて固定された吐出マフラであり、吐出マフラ10は吐出
ポート９を覆っている。11は下軸受８と吐出マフラ10と
の間に形成されたガス室、12は下軸受8,シリンダ５およ
び上軸受７を貫通して設けられ、ガス室11と密閉容器１
内の圧縮機構４外とを連通させる冷媒ガスの逃がし孔で
ある。また、13は圧縮された冷媒ガスを密閉容器１外に
導く吐出管14は密閉容器１外からシリンダ５内へ冷媒ガ
スを導く吸入管である。第６図，第７図は吐出マフラ10
を示し、第６図，第７図において、10aはガス室11を区
切る隔壁で、円周方向の３個所に同形状に形成されてい
る。10bは吐出マフラ10を下軸受８に固定するためのボ
ルト孔、8aは下軸受８のボス部である。 次に、以上のように構成された回転型圧縮機の動作につ
いて説明する。シリンダ５、ローリングピストン６、
上，下軸受7,8によって形成される圧縮室内で、ローリ
ングピストン６が電動機２の回転軸３により偏心回転す
ることで、冷媒ガスが圧縮される。圧縮された冷媒ガス
は、上記圧縮室から吐出ポート９を通って吐出マフラ10
内のガス室11に導かれ、ガス室11内の隔壁10a部を通る
ごとに膨張と収縮を繰り返し、逃がし孔12から圧縮機構
４外の密閉容器１内へ導かれ、さらに吐出管13から密閉
容器１外へ吐出される。FIG. 5 is a vertical sectional view of a conventional rotary compressor disclosed in, for example, Japanese Utility Model Publication No. 60-3351. In FIG. 3, 1 is a closed container, 2 is an electric motor supported and fixed in the closed container 1,
Reference numeral 3 denotes a rotary shaft of the electric motor 2, and 4 denotes a compression mechanism driven by the rotary shaft 3 when the electric motor 2 is driven. The compression mechanism 4 includes the following parts. 5 is a cylinder supported and fixed in the closed container 1, 6 is a rolling piston attached to the rotating shaft 3, 7 is an upper bearing, 8 is a lower bearing, and
The lower bearings 7 and 8 support the rotary shaft 3. Reference numeral 9 denotes a discharge port provided on the lower bearing 8, reference numeral 10 denotes a discharge muffler press-fitted and fixed to the outer peripheral surface of the lower bearing 8, and the discharge muffler 10 covers the discharge port 9. Reference numeral 11 denotes a gas chamber formed between the lower bearing 8 and the discharge muffler, 12 denotes a gas chamber 11 and the hermetically sealed container 1 which are provided so as to penetrate the lower bearing 8, the cylinder 5 and the upper bearing 7.
It is an escape hole for the refrigerant gas that communicates the inside with the outside of the compression mechanism 4. Further, 13 is a discharge pipe for guiding the compressed refrigerant gas to the outside of the closed container 1, and 14 is a suction pipe for guiding the refrigerant gas from the outside of the closed container 1 into the cylinder 5. 6 and 7 show the discharge muffler 10
In FIG. 6 and FIG. 7, 10a is a partition wall that divides the gas chamber 11, and is formed in the same shape at three locations in the circumferential direction. 10b is a bolt hole for fixing the discharge muffler 10 to the lower bearing 8, and 8a is a boss portion of the lower bearing 8. Next, the operation of the rotary compressor configured as described above will be described. Cylinder 5, rolling piston 6,
In the compression chamber formed by the upper and lower bearings 7 and 8, the rolling piston 6 is eccentrically rotated by the rotating shaft 3 of the electric motor 2 to compress the refrigerant gas. The compressed refrigerant gas is discharged from the compression chamber through the discharge port 9 to the discharge muffler 10.
Is guided to the gas chamber 11 inside, and repeats expansion and contraction every time it passes through the partition wall 10a inside the gas chamber 11, is guided from the escape hole 12 into the closed container 1 outside the compression mechanism 4, and is further sealed from the discharge pipe 13. It is discharged to the outside of the container 1.
従来の回転型圧縮機は、以上のように構成され、圧縮さ
れた冷媒ガスが、回転軸３の１回転ごとに吐出ポート９
から吐出マフラ10内に断続的に吹き出されるため、圧力
の変動が激しく、吐出マフラ10が振動したりし、鳴きと
呼ばれる騒音を発生したり、これが密閉容器１に伝わっ
て圧縮機の振動、騒音の原因の１つになるという課題が
あった。 この発明は、上記のような課題を解決するためになされ
たもので、吐出マフラ内での圧縮された吐出ガスの流れ
を制御して、吐出マフラの振動やいわゆる鳴きを低減す
ると共に、回転型圧縮機の効率低下が生じないようにす
ることを目的としている。The conventional rotary compressor is configured as described above, and the compressed refrigerant gas is discharged from the discharge port 9 every rotation of the rotary shaft 3.
Since it is intermittently blown into the discharge muffler 10, the pressure fluctuates drastically, the discharge muffler 10 vibrates, and noise called squeal is generated. There was a problem of becoming one of the causes of noise. The present invention has been made to solve the above problems, and controls the flow of compressed discharge gas in the discharge muffler to reduce the vibration and so-called squeal of the discharge muffler, as well as the rotary type. The purpose is to prevent a decrease in the efficiency of the compressor.
この発明に係る回転型圧縮機は、吐出マフラ内の隔壁と
軸受のボス部との間に形成した冷媒ガス流路の断面積
を、吐出マフラから密閉容器内への冷媒ガス逃がし孔を
囲む部分では、吐出ポートの開口面積と等しくしたもの
である。In the rotary compressor according to the present invention, the cross-sectional area of the refrigerant gas flow path formed between the partition wall in the discharge muffler and the boss portion of the bearing is a portion surrounding the refrigerant gas escape hole from the discharge muffler into the closed container. In, the opening area of the discharge port is made equal.
この発明における回転型圧縮機は、吐出マフラ内の隔壁
と軸受のボス部との間の冷媒ガス流路の断面積を吐出ポ
ートの開口面積と等しくしたので、吐出ポートから吐出
される冷媒ガスの流量に見合う最低の流路を確保して、
圧縮された冷媒ガスの膨張，収縮をスムーズにできるこ
とにより、吐出マフラの振動や鳴きを、圧縮機の効率を
低下させることなく、低減させることができる。In the rotary compressor according to the present invention, since the cross-sectional area of the refrigerant gas flow passage between the partition wall in the discharge muffler and the boss portion of the bearing is made equal to the opening area of the discharge port, the refrigerant gas discharged from the discharge port Secure the lowest flow path that matches the flow rate,
Since the compressed refrigerant gas can be smoothly expanded and contracted, the vibration and squeal of the discharge muffler can be reduced without lowering the efficiency of the compressor.
以下、この発明の一実施例を第１図ないし第４図につい
て説明する。 第１図，第２図はこの発明の一実施例による吐出マフラ
を示す。第１図，第２図において、８は下軸受、8aは下
軸受８の筒状のボス部、10は吐出マフラ、10bは吐出マ
フラ10を下軸受８に固定するボルト（図示省略）のボル
ト孔、10c,10bは吐出マフラ10内に張り出している隔
壁、11は吐出マフラ10と下軸受８とによって形成された
ガス室である。 また、第３図，第４図はこの発明の一実施例の要部を示
す。第３図，第４図において、第１図，第２図と同一符
号は同一部分を示し、９は下軸受８に設けられた吐出ポ
ート、12は吐出マフラ10内のガス室11に溜る冷媒ガスを
圧縮機構外に導く逃がし穴である。そして、R1は吐出マ
フラ10の中心から隔壁10cの先端までの距離、R2は吐出
マフラ10の中心から隔壁10dの先端までの距離であり、R
2＞R1に設定されている。ｒは下軸受８のボス部8aの外
半径であり、隔壁10cの先端とボス部8aの外半径との差
Δｄが冷媒ガス流路となる隙間であり、これらの部分の
断面積が吐出ポート９の吐出マフラ10への開口面積と等
しくなるように、吐出ポート９とほぼ相対する側のガス
逃がし孔12を囲む２個所の隔壁10cについて設定されて
おり、吐出ポート９近くには他の隔壁10dが配設されて
いる。なお、この実施例の上述した以外の構成は、第４
図ないし第６図に示した従来の回転型圧縮機と同様であ
る。 この実施例による回転型圧縮機は、吐出マフラ10内に設
けられた隔壁10cの先端部を下軸受８のボス部8aとの間
に形成される冷媒ガス流路の断面積を吐出ポート９の開
口面積と等しくしたので、吐出マフラ10は、吐出ポート
９から吐出される冷媒ガスの流量に最低必要な流路を確
保して、吐出される冷媒ガスの膨張，収縮をスムーズに
行うことができ、マフラ10としての効果を増すことがで
き、圧縮機の効率を低下させずに、その振動、騒音を低
減させることができる。An embodiment of the present invention will be described below with reference to FIGS. 1 and 2 show a discharge muffler according to an embodiment of the present invention. In FIGS. 1 and 2, 8 is a lower bearing, 8a is a cylindrical boss portion of the lower bearing 8, 10 is a discharge muffler, and 10b is a bolt (not shown) for fixing the discharge muffler 10 to the lower bearing 8. Holes, 10c and 10b are partition walls protruding in the discharge muffler 10, and 11 is a gas chamber formed by the discharge muffler 10 and the lower bearing 8. 3 and 4 show the essential parts of an embodiment of the present invention. In FIGS. 3 and 4, the same reference numerals as those in FIGS. 1 and 2 indicate the same parts, 9 is a discharge port provided in the lower bearing 8, 12 is a refrigerant accumulated in the gas chamber 11 in the discharge muffler 10. It is an escape hole that guides the gas out of the compression mechanism. R 1 is the distance from the center of the discharge muffler 10 to the tip of the partition wall 10c, R 2 is the distance from the center of the discharge muffler 10 to the tip of the partition wall 10d, R
2> is set to R 1. r is the outer radius of the boss portion 8a of the lower bearing 8, and the difference Δd between the tip of the partition wall 10c and the outer radius of the boss portion 8a is a gap that serves as a refrigerant gas flow path, and the cross-sectional area of these portions is the discharge port. The two partition walls 10c surrounding the gas escape holes 12 on the side substantially facing the discharge port 9 are set so as to be equal to the opening area of the discharge muffler 10 in the vicinity of the discharge port 9, and another partition wall near the discharge port 9 is provided. 10d is provided. The configuration of this embodiment other than that described above is similar to that of the fourth embodiment.
This is the same as the conventional rotary compressor shown in FIGS. In the rotary compressor according to this embodiment, the cross-sectional area of the refrigerant gas flow path formed between the tip of the partition wall 10c provided in the discharge muffler 10 and the boss portion 8a of the lower bearing 8 is defined by the discharge port 9. Since the opening area is made equal, the discharge muffler 10 can ensure the flow path of the refrigerant gas discharged from the discharge port 9 that is at least necessary to smoothly expand and contract the discharged refrigerant gas. The effect of the muffler 10 can be increased, and the vibration and noise of the compressor can be reduced without lowering the efficiency of the compressor.
以上説明したように、この発明によれば、吐出マフラ内
に設けた隔壁のうち、冷媒ガス逃がし孔を囲むものと軸
受のボス部との間に形成される冷媒ガス流路の断面積を
吐出ポートの開口面積と等しくしたことにより、吐出マ
フラの効果を高め、その振動、鳴きを低減させることが
でき、したがって、密閉容器の振動、騒音を低減させる
ことが、回転型圧縮機の効率を低下させずにできるとい
う効果がある。As described above, according to the present invention, among the partition walls provided in the discharge muffler, the cross-sectional area of the refrigerant gas flow passage formed between the partition wall surrounding the refrigerant gas escape hole and the boss portion of the bearing is discharged. By making it equal to the opening area of the port, it is possible to enhance the effect of the discharge muffler and reduce its vibration and squeal. Therefore, reducing the vibration and noise of the closed container reduces the efficiency of the rotary compressor. The effect is that you can do without.
第１図はこの発明の一実施例による回転型圧縮機の吐出
マフラを示す底面図、第２図は同側断面図、第３図は同
吐出マフラと下軸受を示す底面図、第４図は第３図IV部
の断面図、第５図は従来の回転型圧縮機を示す縦断面
図、第６図は第５図の吐出マフラを示す底面図、第７図
は同側断面図である。 １……密閉容器、２……電動機、３……圧縮機構、８…
…下軸受、8a……ボス部、９……吐出ポート、10……吐
出マフラ、10c,10d……隔壁、11……ガス室、12……冷
媒ガス逃がし孔。 なお、図中同一符号は同一又は相当部分を示す。FIG. 1 is a bottom view showing a discharge muffler of a rotary compressor according to an embodiment of the present invention, FIG. 2 is a side sectional view of the same, FIG. 3 is a bottom view showing the discharge muffler and a lower bearing, and FIG. 3 is a sectional view of IV part in FIG. 3, FIG. 5 is a longitudinal sectional view showing a conventional rotary compressor, FIG. 6 is a bottom view showing the discharge muffler of FIG. 5, and FIG. 7 is a sectional view of the same side. is there. 1 ... airtight container, 2 ... electric motor, 3 ... compression mechanism, 8 ...
… Lower bearing, 8a …… Boss part, 9 …… Discharge port, 10 …… Discharge muffler, 10c, 10d …… Differential wall, 11 …… Gas chamber, 12 …… Refrigerant gas escape hole. The same reference numerals in the drawings indicate the same or corresponding parts.
Claims (1)
電動機と、上記密閉容器内に設けられ上記電動機の回転
軸によって駆動される圧縮機構とを備え、この圧縮機構
に設けられ上記回転軸を軸支する軸受に吐出ポートを設
け、この吐出ポートを覆うように上記軸受の外側に吐出
マフラを固定した回転型圧縮機において、上記吐出マフ
ラ内の隔壁と軸受のボス部との間に形成した冷媒ガス流
路の断面積を、吐出マフラから密閉容器内への冷媒ガス
逃がし孔を囲む部分では、上記吐出ポートの開口面積と
等しくしたことを特徴とする回転型圧縮機。1. A hermetically sealed container, an electric motor provided in the hermetically sealed container, and a compression mechanism provided in the hermetically sealed container and driven by a rotating shaft of the electric motor. In a rotary compressor in which a discharge port is provided on a bearing that supports the shaft, and a discharge muffler is fixed outside the bearing so as to cover the discharge port, between the partition wall in the discharge muffler and the boss portion of the bearing. A rotary compressor, wherein a cross-sectional area of the formed refrigerant gas flow passage is equal to an opening area of the discharge port in a portion surrounding the refrigerant gas escape hole from the discharge muffler into the closed container.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP406888A JPH0758076B2 (en) | 1988-01-12 | 1988-01-12 | Rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP406888A JPH0758076B2 (en) | 1988-01-12 | 1988-01-12 | Rotary compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01182595A JPH01182595A (en) | 1989-07-20 |
| JPH0758076B2 true JPH0758076B2 (en) | 1995-06-21 |
Family
ID=11574505
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP406888A Expired - Lifetime JPH0758076B2 (en) | 1988-01-12 | 1988-01-12 | Rotary compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0758076B2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007132226A (en) * | 2005-11-09 | 2007-05-31 | Sanyo Electric Co Ltd | Rotary compressor |
| JP7204446B2 (en) * | 2018-11-28 | 2023-01-16 | 日立ジョンソンコントロールズ空調株式会社 | electric rotary compressor |
-
1988
- 1988-01-12 JP JP406888A patent/JPH0758076B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH01182595A (en) | 1989-07-20 |
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