JPS62170796A - Rotary compressor - Google Patents
Rotary compressorInfo
- Publication number
- JPS62170796A JPS62170796A JP1405286A JP1405286A JPS62170796A JP S62170796 A JPS62170796 A JP S62170796A JP 1405286 A JP1405286 A JP 1405286A JP 1405286 A JP1405286 A JP 1405286A JP S62170796 A JPS62170796 A JP S62170796A
- Authority
- JP
- Japan
- Prior art keywords
- ribs
- circumference
- section
- deformation
- vibration
- 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 7
- 238000007906 compression Methods 0.000 claims description 7
- 239000003507 refrigerant Substances 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 238000013016 damping Methods 0.000 description 3
- 230000010349 pulsation Effects 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 239000010721 machine oil Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 230000000087 stabilizing effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は、冷凍冷蔵装置に用いられる回転型圧縮機に関
する。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a rotary compressor used in a freezing and refrigeration system.
従来の技術
近年、冷凍冷蔵装置に用いられる圧縮機は、省エネルギ
ー、省スペースの見地より往復型から回2ベーノ
転型へ移行しつつある。これらの回転型圧縮機は通常、
電動圧縮要素を、電動機ステータ及び軸受あるいはシリ
ンダを焼バメあるいは溶接するどとにより、密閉ケース
に固定している。そのため、電動圧縮要素にて生じた振
動はスプリング等により吸振されることなく密閉ケース
に伝わるため、密閉ケースを振動させて大きな騒音を発
生することがあった。BACKGROUND OF THE INVENTION In recent years, compressors used in refrigeration systems have been shifting from reciprocating type to bi-vane type compressors from the viewpoint of energy saving and space saving. These rotary compressors are typically
The electric compression element is fixed to the closed case by shrink fitting or welding the electric motor stator and bearing or cylinder. Therefore, the vibrations generated by the electric compression element are transmitted to the sealed case without being absorbed by the spring or the like, which may cause the sealed case to vibrate and generate large noise.
以下、図面を参照しながら、上述した従来の回転型圧縮
機の一例について説明する。An example of the conventional rotary compressor mentioned above will be described below with reference to the drawings.
第4図は従来の回転型圧縮機の一例を示すものである。FIG. 4 shows an example of a conventional rotary compressor.
図において、1は回転型圧縮機である。In the figure, 1 is a rotary compressor.
2は電動機で3はステータ、4はロータ、5はステータ
の巻線である。6は圧縮要素で、7はロータ4に固定し
たクランクシャフト、8,9はクランクシャフト7を支
持する軸受、1oはシリンダ、11はクランクシャフト
のクランク部7aの周りを摺動自在のピストンである。2 is an electric motor, 3 is a stator, 4 is a rotor, and 5 is a winding of the stator. 6 is a compression element, 7 is a crankshaft fixed to the rotor 4, 8 and 9 are bearings that support the crankshaft 7, 1o is a cylinder, and 11 is a piston that is slidable around the crank portion 7a of the crankshaft. .
12Fi吐出カバーで、14はクランクシャフト7に継
接されたスプリング13を包含した給油管である。15
は剛材3ベーノ
からなる密閉ケースで、ステータ3と軸受8を内接固定
する厚さ2.5咽の円筒部16とカップ状の厚さ3wn
の蓋部17,18からなる。19は吸入管、20は吐出
管で、21は冷凍機油である。In the 12Fi discharge cover, 14 is an oil supply pipe that includes a spring 13 connected to the crankshaft 7. 15
is a sealed case made of three rigid materials, which includes a cylindrical part 16 with a thickness of 2.5mm and a cup-shaped part with a thickness of 3wn, which internally fixes the stator 3 and the bearing 8.
It consists of lid parts 17 and 18. 19 is a suction pipe, 20 is a discharge pipe, and 21 is refrigerating machine oil.
以上のように構成された回転型圧縮機について、以下そ
の動作について説明する。The operation of the rotary compressor configured as above will be described below.
主として、シリンダ10内での冷媒の圧縮により生じた
冷媒の圧力脈動や、機械的な振動は、各部品を振動させ
軸受8あるいは密閉ケース14内の冷媒を伝播して密閉
ケース14に伝わる。そのだめ、密閉ケース15が振動
し、騒音を発生する。Mainly, refrigerant pressure pulsations and mechanical vibrations caused by compression of the refrigerant in the cylinder 10 vibrate each component and propagate through the bearing 8 or the refrigerant in the closed case 14 and are transmitted to the closed case 14. Unfortunately, the sealed case 15 vibrates and generates noise.
発明が解決しようとする問題点
密閉ケース15は、I KHz−2KHzの周波数まで
の周波数領域では変形をともなわない剛体振動をするが
、それ以上の周波数領域では変形を伴なう弾性振動をす
る。Problems to be Solved by the Invention The sealed case 15 undergoes rigid body vibration without deformation in the frequency range up to I KHz-2 KHz, but undergoes elastic vibration accompanied by deformation in the frequency range above that.
密閉ケース15は、円筒部16にステータ3や軸受10
を内接固定しているため、密閉ケース15の円形断面の
変形を伴なう弾性振動は5KHz以上の高周波数領域に
て発生し、2に〜5KHzの周波数領域では第5図に示
すような軸方向の変形を伴なう弾性振動が主体である。The sealed case 15 includes the stator 3 and the bearing 10 in the cylindrical part 16.
is internally fixed, elastic vibration accompanied by deformation of the circular cross section of the sealed case 15 occurs in the high frequency range of 5 KHz or higher, and in the frequency range of 2 to 5 KHz, as shown in Fig. 5. The main vibration is elastic vibration accompanied by axial deformation.
なお、第5図においてAは変形していない形状、Bは変
形した形状を示す。In addition, in FIG. 5, A shows an undeformed shape, and B shows a deformed shape.
そのため、2に〜5KHz 間では主として密閉ケー
スの軸方向断面の変形による振動、5KHz以上ではさ
らに密閉ケースの円形断面の変形を伴なう振動による騒
音が発生する。Therefore, between 2 and 5 kHz, vibrations occur mainly due to the deformation of the axial cross section of the sealed case, and above 5 kHz, noise is generated due to vibrations accompanied by the deformation of the circular cross section of the sealed case.
本発明は、上記問題点に鑑み、圧縮機効率を低下するこ
となく、さらに圧縮機のコンパクト性をほとんどそこな
うことなく、極めて効果的な圧縮機騒音低減効果を提供
するものである。In view of the above-mentioned problems, the present invention provides an extremely effective compressor noise reduction effect without reducing compressor efficiency and without substantially impairing the compactness of the compressor.
問題点を解決するだめの手段
上記問題点を解決するだめに本発明の回転型圧縮機は、
密閉ケースの円筒部に、円周を不均等に分割する位置に
外周方向に突出し一端部付近から中央部より他端部側に
連なる軸方向の複数のリブ及びこれらのリブとは重なら
ず円周を不均等に分割する位置に外周方向に突出し前記
他端部付近から中央部より前記一端部側に連なる軸方向
の複数6ページ
のリブを備えだものである。Means for Solving the Problems In order to solve the above problems, the rotary compressor of the present invention has the following features:
The cylindrical part of the sealed case has a plurality of ribs in the axial direction that protrude toward the outer circumference at positions that unevenly divide the circumference and extend from the vicinity of one end to the center and the other end, and a circular rib that does not overlap with these ribs. It is provided with a plurality of six pages of ribs in the axial direction that protrude in the outer circumferential direction at positions that divide the circumference unevenly and extend from near the other end to the center and toward the one end.
作 用
本発明は上記した構成によって、密閉ケースの軸方向断
面の変形を伴う振動と円形断面の変形を伴なう振動を高
い周波数領域にずらし、可聴周波数領域の騒音の低減を
図るものである。Function The present invention aims at reducing noise in the audible frequency range by shifting vibrations accompanied by deformation of the axial cross-section of the sealed case and vibrations accompanied by deformation of the circular cross-section to a high frequency range, using the above-described configuration. .
実施例
以下本発明の一実施例の回転型圧縮機について、図面を
参照しながら説明する。尚、説明の重複をさけるため、
従来例と同一部分については同一符号を付し説明を省略
する。EXAMPLE Hereinafter, a rotary compressor according to an example of the present invention will be described with reference to the drawings. In addition, to avoid duplication of explanation,
The same parts as in the conventional example are given the same reference numerals, and the explanation will be omitted.
第1図〜第3図は本発明の回転型圧縮機の一実施例を示
すものである。図において、22は鋼材からなる密閉ケ
ースで、23は厚さ2.5朝の円筒部、24.25は厚
さ3喘のカップ状の蓋部である。円筒部23には、円周
を不均等に分割する位置に外周方向に突出し、一方の端
部23a付近から中央部よりもう一方の端部23b側に
連なる4個のリブ23cが設けられている。これらのリ
ブ23cは円筒部23を円周方向に6:4:5:36
ページ
の割合で不均等に分割するよう配置されている。1 to 3 show an embodiment of a rotary compressor of the present invention. In the figure, 22 is a closed case made of steel, 23 is a cylindrical part with a thickness of 2.5 mm, and 24.25 is a cup-shaped lid part with a thickness of 3 mm. The cylindrical portion 23 is provided with four ribs 23c that protrude toward the outer circumference at positions that divide the circumference unevenly and extend from near one end 23a to the other end 23b from the center. . These ribs 23c extend around the cylindrical portion 23 in a 6:4:5:36 direction in the circumferential direction.
Arranged to divide the page proportions unevenly.
さらに円筒部23には、円周を不均等に分割する位置に
外周方向に突出し、端部23b付近から中央部より端部
23a側に連々る4個のリブ23dが設けられている。Further, the cylindrical portion 23 is provided with four ribs 23d that protrude in the outer circumferential direction at positions that divide the circumference unevenly and extend from near the end 23b to the center toward the end 23a.
これらのリブ23dは円筒部23を、リブ23cとは反
対廻りに円周方向を6:4:5:3の割合で不均等に分
割し、リブ23cとは重ならないよう配置されている。These ribs 23d divide the cylindrical portion 23 unevenly in the circumferential direction in the opposite direction from the ribs 23c at a ratio of 6:4:5:3, and are arranged so as not to overlap with the ribs 23c.
以上のように構成された回転型圧縮機について、以下に
その動作を説明する。The operation of the rotary compressor configured as above will be explained below.
主として、シリンダ10内での冷媒の圧縮により生じた
冷媒の圧力脈動や、機械的な振動は、各部品を振動させ
軸受8あるいは密閉ケース22内の冷媒を伝播して密閉
ケース22に伝わる。そのため、密閉ケース22が振動
し騒音を発生する。Mainly, refrigerant pressure pulsations and mechanical vibrations caused by compression of the refrigerant within the cylinder 10 vibrate each component and propagate through the bearing 8 or the refrigerant within the closed case 22 and are transmitted to the closed case 22. Therefore, the sealed case 22 vibrates and generates noise.
密閉ケース22は、1に〜2KHzの周波数までの周波
数領域では変形をともなわない剛体振動をするが、それ
以上の周波数領域では変形を伴なう弾性振動をする。密
閉ケース22は、円筒部23にステータ3や軸受1oを
内接固定しているだめ、7へ一ン
弾性振動は低い周波数では軸方向の変形によるものが主
体であり、周波数が高くなるようにつれ円形断面の変形
によるものが現れる。しかし円筒部23には軸方向のリ
ブ23C及び23dが設けであるので、密閉ケース22
は軸方向断面の変形に対して剛性的に強くなっているた
め、リブ23C223dのない場合に比べて軸方向断面
変形による固有振動数は高くなる。The sealed case 22 performs rigid body vibration without deformation in a frequency range of 1 to 2 kHz, but performs elastic vibration with deformation in a frequency range higher than that. In the sealed case 22, the stator 3 and the bearing 1o are internally fixed in the cylindrical part 23, so the elastic vibration is mainly due to axial deformation at low frequencies, and as the frequency increases, Some appear due to deformation of the circular cross section. However, since the cylindrical portion 23 is provided with ribs 23C and 23d in the axial direction, the closed case 22
Since the ribs 23C and 223d are rigidly strong against deformation in the axial cross section, the natural frequency due to the deformation in the axial cross section becomes higher than in the case where there is no rib 23C223d.
さらに、リブ23C223dは円周を不均等に分割する
よう配置されているだめ、円形断面の変形による振動は
、完全軸対称のモードをとれなくなるため、固有振動数
は高くなる。Further, since the ribs 23C223d are arranged so as to divide the circumference unevenly, the vibration due to the deformation of the circular cross section cannot take a perfectly axially symmetrical mode, so that the natural frequency becomes high.
しかも、リブ23Cとリブ23dは、互いに重なること
なく、円周断面を異なった分割とするよう配置されてい
るため、端部23a側と端部23b側の円形断面変形に
よる振動は、それぞれ他端部23b側、23a側の円形
断面変形による振動を励起しにくく、ダンピング効果が
働くため、同一加振力に対して円形断面の変形はきわめ
て振幅の小さいものとなる。Moreover, since the ribs 23C and 23d are arranged so that the circumferential cross section is divided into different sections without overlapping each other, the vibrations due to the circular cross-sectional deformation on the end 23a side and the end 23b side are transmitted to the other end. It is difficult to excite vibration due to the circular cross-sectional deformation on the portions 23b and 23a sides, and a damping effect is exerted, so that the amplitude of the circular cross-sectional deformation is extremely small for the same excitation force.
以上のように本実施例によれば、密閉ケース22の円筒
部23に、円周を不均等に分割する位置に外周方向に突
出し、端部23a付近から中央部より他の端部23b側
に連なる軸方向の複数のリブ23c及びこれらのリブ2
3cとは重ならず円周を不均等に分割する位置に外周方
向に突出し、端部23b付近から中央部より端部23a
側に連なる軸方向の複数のリブ2sdを設けることによ
り、密閉ケース22の軸方向断面及び円形断面の変形に
よる固有振動数を高い周波数領域にずらし可聴周波数領
域の固有振動モードを減少させることができ、さらにダ
ンピング効果により円形断面の変形による振動の振幅を
減少させることができ、圧縮機効率を損なうことなく、
まだ圧縮機のコンパクト性をほとんど損なうことなく圧
縮機騒音を安定して低減するものである。As described above, according to this embodiment, the cylindrical portion 23 of the sealed case 22 has protrusions in the outer circumferential direction at positions that divide the circumference unevenly, and extends from near the end 23a to the other end 23b from the center. A plurality of consecutive ribs 23c in the axial direction and these ribs 2
3c, but protrudes in the outer circumferential direction at a position that divides the circumference unevenly, and from near the end 23b to the center from the end 23a.
By providing a plurality of ribs 2sd in the axial direction connected to the side, it is possible to shift the natural frequency due to deformation of the axial cross section and circular cross section of the sealed case 22 to a high frequency region, and reduce the natural vibration mode in the audible frequency region. , Furthermore, the damping effect can reduce the vibration amplitude due to the deformation of the circular cross section, without compromising the compressor efficiency.
Still, compressor noise can be stably reduced without compromising the compactness of the compressor.
発明の効果
以上のように本発明は、密閉ケース内に電動圧縮要素を
収納する回転型圧縮機において、密閉ケースの円筒部に
、円周を不均等に分割する位置に9ページ
外周方向に突出し一端部付近から中央部より他端部側に
連なる軸方向の複数のリブ及びこれらのリブとは重なら
ず円周を不均等に分割する位置に外周方向に突出し前記
他端部付近から中央部より前記一端部側に連なる軸方向
の複数のリブを設けることにより、密閉ケースの軸方向
断面の変形、及び円形断面の変形による固有振動数を高
い周波数領域にずらし可聴周波数領域の固有振動モード
を減少させることができ、さらにダンピング効果により
円形断面の変形による振動の振幅を減少させることがで
き、圧縮機効率を損うことなく、また圧縮機のコンパク
ト性をほとんど損なうことなく圧縮機騒音を安定して低
減するものである。Effects of the Invention As described above, the present invention provides a rotary compressor in which an electric compression element is housed in a sealed case. A plurality of ribs extending in the axial direction from near one end to the center from the other end, and a plurality of ribs that do not overlap with these ribs and protrude in the outer circumferential direction at positions that unevenly divide the circumference from near the other end to the center. By providing a plurality of ribs in the axial direction connected to the one end side, the natural frequency due to the deformation of the axial cross section of the sealed case and the deformation of the circular cross section is shifted to a higher frequency region, and the natural vibration mode in the audible frequency region is shifted. Furthermore, the damping effect can reduce the vibration amplitude due to the deformation of the circular cross section, stabilizing the compressor noise without compromising the compressor efficiency or almost impairing the compactness of the compressor. It is intended to reduce the
第1図は本発明の一実施例を示す回転型圧縮機の密閉ケ
ースの円筒部斜視図、第2図は第1図の1−1’線にお
ける断面図、第3図は同圧縮機の断面図、第4図は従来
例の回転型圧縮機の断面図、第5図は同圧縮機の密閉ケ
ースの軸方向断面の変形による固有振動モードを示す図
である。
10ベーノ
3・・・・・・ステータ、8・・・・・・軸受、22・
・・・・・密閉ケース、23・・・・・・円筒部、23
C・・・・・・リブ、23d・・・・・・リブ。Fig. 1 is a perspective view of a cylindrical part of a sealed case of a rotary compressor showing an embodiment of the present invention, Fig. 2 is a sectional view taken along line 1-1' in Fig. 4 is a sectional view of a conventional rotary compressor, and FIG. 5 is a diagram showing natural vibration modes due to deformation of the axial cross section of the closed case of the same compressor. 10 Beno 3... Stator, 8... Bearing, 22...
... Sealed case, 23 ... Cylindrical part, 23
C...Rib, 23d...Rib.
Claims (1)
方向に突出し一端部付近から中央部より他端部側に連な
る軸方向の複数のリブ及びこれらのリブとは重ならず円
周を不均等に分割する位置に外周方向に突出し前記他端
部付近から中央部より前記一端部側に連なる軸方向の複
数のリブを有する略円筒部とカップ状の蓋部とで密閉ケ
ースを形成し、この密閉ケース内に収納される電動圧縮
要素を備えた回転型圧縮機。Both ends are circular, and a plurality of ribs in the axial direction protrude toward the outer circumference at positions that unevenly divide the circumference and extend from the vicinity of one end to the center and the other end, and these ribs do not overlap and are circular. A sealed case is formed by a substantially cylindrical portion having a plurality of ribs in the axial direction protruding toward the outer circumference at positions that divide the circumference unevenly and extending from near the other end to the central portion toward the one end, and a cup-shaped lid portion. A rotary compressor with an electric compression element formed and housed within this closed case.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP1405286A JPS62170796A (en) | 1986-01-24 | 1986-01-24 | Rotary compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP1405286A JPS62170796A (en) | 1986-01-24 | 1986-01-24 | Rotary compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS62170796A true JPS62170796A (en) | 1987-07-27 |
Family
ID=11850318
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP1405286A Pending JPS62170796A (en) | 1986-01-24 | 1986-01-24 | Rotary compressor |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS62170796A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2008102841A1 (en) * | 2007-02-21 | 2008-08-28 | Mitsubishi Heavy Industries, Ltd. | Compressor |
-
1986
- 1986-01-24 JP JP1405286A patent/JPS62170796A/en active Pending
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2008102841A1 (en) * | 2007-02-21 | 2008-08-28 | Mitsubishi Heavy Industries, Ltd. | Compressor |
JP2008202522A (en) * | 2007-02-21 | 2008-09-04 | Mitsubishi Heavy Ind Ltd | Compressor |
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