JP2000018184A - Rotary compressor - Google Patents
Rotary compressorInfo
- Publication number
- JP2000018184A JP2000018184A JP10184816A JP18481698A JP2000018184A JP 2000018184 A JP2000018184 A JP 2000018184A JP 10184816 A JP10184816 A JP 10184816A JP 18481698 A JP18481698 A JP 18481698A JP 2000018184 A JP2000018184 A JP 2000018184A
- Authority
- JP
- Japan
- Prior art keywords
- muffler
- discharge port
- rotary compressor
- compression mechanism
- noise
- 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
Landscapes
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明は、ロータリコンプ
レッサに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor.
【０００２】[0002]
【従来の技術】一般に、ロータリコンプレッサにあって
は、電動機部と、電動機部によって回転動力が与えられ
る圧縮機構部とから成り、圧縮機構部で圧縮された冷媒
ガスは、吐出ポートから吐出されると共に、吐出ポート
はマフラにより覆われている。2. Description of the Related Art Generally, a rotary compressor comprises an electric motor section and a compression mechanism section to which rotational power is applied by the electric motor section, and refrigerant gas compressed by the compression mechanism section is discharged from a discharge port. At the same time, the discharge port is covered with a muffler.
【０００３】[0003]
【発明が解決しようとする課題】圧縮機構部で圧縮され
た冷媒ガスは、吐出ポートから急激にマフラ内空間に吐
出されると膨張し、大きな音を発生するため、マフラに
より消音が図られている。The refrigerant gas compressed by the compression mechanism expands when it is rapidly discharged from the discharge port into the muffler internal space, and generates a loud noise. I have.
【０００４】図１３は円形状に形成されたマフラ１０１
を上からみたもので、点線で示す如く吐出ポート１０３
から吐出された冷媒ガスを急激に膨張させて圧力を下げ
て消音する膨張型マフラとして機能する。FIG. 13 shows a muffler 101 formed in a circular shape.
From the top, as shown by the dotted line in FIG.
It functions as an expansion type muffler that rapidly expands the refrigerant gas discharged from the, reduces the pressure, and silences.
【０００５】ところで、膨張型マフラにおいて、周方向
の１次共鳴モードを考えた場合、音響的加振位置となる
吐出ポート１０３と、この吐出ポート１０３に対して周
方向に約１８０度移動した位置が、モードの腹（図１３
に示すプラス又はマイナスの位置）となり、大きな音圧
が励起される。この時、マフラ１０１内の固有の音響的
な共鳴周波数の付近の領域では、騒音・振動が増大する
問題があった。By the way, in the expansion type muffler, when considering the primary resonance mode in the circumferential direction, the discharge port 103 serving as an acoustically oscillating position, and the position shifted by about 180 degrees in the circumferential direction with respect to the discharge port 103. Is the mode belly (Fig. 13
(Positive or negative position shown in FIG. 3), and a large sound pressure is excited. At this time, there is a problem that noise and vibration increase in a region near the inherent acoustic resonance frequency in the muffler 101.
【０００６】そこで、この発明は、膨張型マフラとして
機能させながら、マフラ内共鳴周波数付近の音圧値を下
げて騒音を低減させることが出来るようにしたロータリ
コンプレッサを提供することを目的としている。Accordingly, an object of the present invention is to provide a rotary compressor which can reduce noise by lowering a sound pressure value near a resonance frequency in a muffler while functioning as an expansion type muffler.
【０００７】[0007]
【課題を解決するための手段】前記目的を達成するため
に、この発明の請求項１にあっては、吐出ポートを有す
る圧縮機構部に、前記吐出ポートを覆うと共に圧縮機構
部のシャフト軸心を中心とする円形状に形成されたマフ
ラを設置し、そのマフラに、前記吐出ポートに対してシ
ャフト軸心を挟んで周方向に約１８０度移動した位置に
マフラ吐出口を設ける。According to a first aspect of the present invention, there is provided a compression mechanism having a discharge port, wherein the compression mechanism includes a discharge port and covers the discharge port. A muffler formed in a circular shape with the center as a center is provided, and a muffler discharge port is provided on the muffler at a position shifted by about 180 degrees in the circumferential direction with respect to the discharge port with respect to the shaft axis.
【０００８】これにより、吐出ポートからの冷媒ガス
は、膨脹型マフラとして機能するマフラ内に吐出され、
マフラ吐出口からの音は減衰される。一方、マフラ内に
おいて、音圧値が高くなる位置に吐出口を設けたので、
そこでの圧力が下がって、マフラ内の周方向共鳴周波数
付近の騒音とそれに起因する振動を小さく抑える大幅な
騒音低減効果を得ることができる。Thus, the refrigerant gas from the discharge port is discharged into a muffler functioning as an expansion muffler,
Sound from the muffler outlet is attenuated. On the other hand, in the muffler, the discharge port is provided at a position where the sound pressure value becomes high,
The pressure there is reduced, and a significant noise reduction effect can be obtained in which noise around the circumferential resonance frequency in the muffler and vibration caused by the noise are reduced.
【０００９】また、この発明の請求項２にあっては、マ
フラ吐出口を、円形状に形成されたマフラの外周縁に寄
せた位置に設ける。According to a second aspect of the present invention, the muffler discharge port is provided at a position close to the outer peripheral edge of the circular muffler.
【００１０】これにより、音圧値が高くなる音圧をマフ
ラの外周縁に寄せてマフラ吐出口を設けたので、そこで
の圧力を有効に下げることができるため、マフラ内の周
方向共鳴周波数付近の騒音とそれに起因する振動を小さ
く抑えることが出来る。Since the muffler discharge port is provided by bringing the sound pressure at which the sound pressure value increases to the outer peripheral edge of the muffler, the pressure there can be effectively reduced. Noise and vibrations caused by the noise can be suppressed.
【００１１】また、この発明の請求項３にあっては、マ
フラ吐出口を、周方向に長い長円の形状とする。According to a third aspect of the present invention, the muffler discharge port is formed in an oval shape that is long in the circumferential direction.
【００１２】これにより、マフラ吐出口での圧力をさら
に低減させて大幅な騒音低減効果を得ることができる。Thus, the pressure at the muffler discharge port can be further reduced, and a significant noise reduction effect can be obtained.
【００１３】また、この発明の請求項４にあっては、マ
フラ吐出口を、１つとする。Further, in the present invention, the number of muffler discharge ports is one.
【００１４】これにより、吐出ポートからマフラ吐出口
までのマフラ内空間の距離を長くすることが可能とな
る。これにより、膨張空間が長くなり、騒音低減効果を
増すことができる。Thus, the distance in the muffler space from the discharge port to the muffler discharge port can be increased. Thereby, the expansion space becomes long, and the noise reduction effect can be increased.
【００１５】また、この発明の請求項５にあっては、吐
出ポートを有する圧縮機構部に、前記吐出ポートを覆う
と共に圧縮機構部のシャフト軸心を中心とする円形状に
形成された第１マフラと第２マフラを設け、前記第１マ
フラに、吐出ポートに対してシャフト軸心を挟んで周方
向に約１８０度移動した位置にマフラ吐出口を設け、第
２マフラに、前記第１マフラのマフラ吐出口から周方向
に６０〜９０度移動した位置に第２マフラのマフラ吐出
口を設ける。According to a fifth aspect of the present invention, the compression mechanism having a discharge port has a first shape which covers the discharge port and has a circular shape centered on a shaft axis of the compression mechanism. A muffler and a second muffler are provided, and a muffler discharge port is provided in the first muffler at a position shifted by about 180 degrees in a circumferential direction with respect to a discharge port across a shaft axis, and the second muffler is provided with the first muffler. The muffler discharge port of the second muffler is provided at a position shifted from the muffler discharge port in the circumferential direction by 60 to 90 degrees.
【００１６】また、この発明の請求項６にあっては、マ
フラ内空間の高さを約１６ｍｍ以下とする。According to a sixth aspect of the present invention, the height of the space inside the muffler is set to about 16 mm or less.
【００１７】これにより、コンプレッサの密閉ケース内
を振動・騒音が伝達し、外部へ放射されにくい６ｋＨｚ
以上の高さ方向共鳴周波数にすることが可能となり、主
にコンプレッサ騒音の大きな原因である４ｋＨｚ，５ｋ
Ｈｚ帯域での高さ方向共鳴周波数を無くして効果的な騒
音低減が図れる。Thus, vibration and noise are transmitted through the sealed case of the compressor, and are hardly radiated to the outside at 6 kHz.
The above resonance frequency in the height direction can be set, and 4 kHz and 5 kHz, which are mainly causes of compressor noise, can be obtained.
Effective noise reduction can be achieved by eliminating the height direction resonance frequency in the Hz band.
【００１８】また、この発明の請求項７にあっては、マ
フラ内空間を高さ方向に仕切り、１つのマフラ内空間の
高さを約１６ｍｍ以下とする。According to a seventh aspect of the present invention, the space inside the muffler is partitioned in the height direction, and the height of one space inside the muffler is set to about 16 mm or less.
【００１９】これにより、コンプレッサの密閉ケース内
を振動・騒音が伝達し、外部へ放射されにくい６ｋＨｚ
以上の高さ方向共鳴周波数にすることが可能となり、４
ｋＨｚ，５ｋＨｚ付近の音圧が低減する。Thus, vibration and noise are transmitted in the sealed case of the compressor and are hardly radiated to the outside at 6 kHz.
The above resonance frequency in the height direction can be obtained,
The sound pressure around kHz and 5 kHz is reduced.
【００２０】また、この発明の請求項８にあっては、マ
フラ内空間は、仕切部材により高さ方向に仕切ることで
構成される。Further, according to claim 8 of the present invention, the inner space of the muffler is constituted by partitioning in the height direction by a partition member.
【００２１】これにより、マフラ内を仕切り部材により
容易に２段に仕切ることが出来るので安価なマフラ構成
を実現できる。Thus, the inside of the muffler can be easily divided into two stages by the partition member, so that an inexpensive muffler configuration can be realized.
【００２２】また、この発明の請求項９にあっては、マ
フラは、第１マフラと第２マフラとによる２ピースで構
成され、第１マフラの外周縁外面と第２マフラの外周縁
内面とを互いに隙間がないように密着結合する。According to a ninth aspect of the present invention, the muffler is composed of two pieces of a first muffler and a second muffler, and has an outer peripheral edge outer surface of the first muffler and an outer peripheral inner surface of the second muffler. Are tightly bonded to each other so that there is no gap between them.
【００２３】これにより、第１，第２マフラを重ね合わ
せることで２段マフラの組立が簡単にできる。Thus, the two-stage muffler can be easily assembled by overlapping the first and second mufflers.
【００２４】また、この発明の請求項１０にあっては、
請求項６において、マフラは、少なくとも第１マフラと
第２マフラとから構成され、前記第１マフラに、吐出ポ
ートに対してシャフト軸心を挟んで周方向に約１８０度
移動した位置に吐出口を設け、第２マフラのマフラ吐出
口を、前記第１マフラのマフラ吐出口から周方向に６０
〜９０度移動した位置に配置する。According to a tenth aspect of the present invention,
7. The muffler according to claim 6, wherein the muffler is composed of at least a first muffler and a second muffler, and the discharge port is moved to the first muffler at a position shifted by about 180 degrees in a circumferential direction with respect to a discharge port across a shaft axis. Is provided, and the muffler discharge port of the second muffler is circumferentially moved 60 m from the muffler discharge port of the first muffler.
It is arranged at a position shifted by 90 degrees.
【００２５】[0025]
【発明の実施の形態】以下、図１乃至図７の図面を参照
しながらこの発明の第１の実施形態について具体的に説
明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a first embodiment of the present invention will be described in detail with reference to FIGS.
【００２６】図１において、１はロータリコンプレッサ
３の密閉ケースを示している。密閉ケース１は、上端部
に吐出管５を有すると共に、内部には、電動機構部７と
圧縮機構部９がそれぞれ配置されている。In FIG. 1, reference numeral 1 denotes a sealed case of the rotary compressor 3. The sealed case 1 has a discharge pipe 5 at the upper end, and an electric mechanism 7 and a compression mechanism 9 are respectively disposed inside.
【００２７】電動機構部７は、密閉ケース１の内壁面に
固着されたステータ１１と、シャフト１３に装着された
ロータ１５とから成り、ステータ１１が通電されること
でロータ１５を介して前記シャフト１３に回転動力が与
えられるようになっている。The electric mechanism 7 comprises a stator 11 fixed to the inner wall surface of the sealed case 1 and a rotor 15 mounted on the shaft 13. 13 is provided with rotational power.
【００２８】圧縮機構部９は、フレーム１５を介して密
閉ケース１の内壁面に固着されたシリンダ１７と、シリ
ンダ１７内に配置されたローラ１９とで構成され、ロー
ラ１９は、前記シャフト１３に設けられた偏心軸部２１
に嵌挿され、偏心軸部２１の回転によって偏心回転が与
えられるようになっている。The compression mechanism 9 comprises a cylinder 17 fixed to the inner wall surface of the sealed case 1 via a frame 15 and a roller 19 disposed in the cylinder 17. Eccentric shaft part 21 provided
And the eccentric shaft 21 is rotated by the rotation of the eccentric shaft 21.
【００２９】シャフト１３は、主軸受部材２３と副軸受
部材２５とにより回転自在に軸支され、主軸受部材２３
には吐出ポート２７が設けられている。The shaft 13 is rotatably supported by a main bearing member 23 and a sub-bearing member 25.
Is provided with a discharge port 27.
【００３０】シリンダ１７には、吸込管２９と連通し合
う吸込ポート３１と、ばね等による付勢手段によって前
記ローラ１９の外周面と常時接触し合うブレード（図示
していない）が設けられ、シリンダ１７、ローラ１９及
びブレードとにより圧縮室３３が作られるようになって
いる。The cylinder 17 is provided with a suction port 31 communicating with the suction pipe 29 and a blade (not shown) which is always in contact with the outer peripheral surface of the roller 19 by a biasing means such as a spring. A compression chamber 33 is formed by the 17, the roller 19 and the blade.
【００３１】圧縮室３３は、前記吐出ポート２７と連通
し、吐出ポート２７はマフラ３５により覆われると共
に、吐出弁３７と吐出弁３７の開度を制限する弁ストッ
パー３９を有している。The compression chamber 33 communicates with the discharge port 27. The discharge port 27 is covered with a muffler 35 and has a discharge valve 37 and a valve stopper 39 for limiting the opening of the discharge valve 37.
【００３２】マフラ３５は、前記主軸受部材２３を貫通
した貫通孔４１のシャフト軸心Ｘを中心とする円形状に
形成され、内部は環状空間となっていて膨張型マフラの
マフラ室４３となっている。マフラ３５の周縁フランジ
は、ボルト４５により前記主軸受部材２３に固着され、
上面には、マフラ吐出口４７が設けられている。The muffler 35 is formed in a circular shape centered on the shaft axis X of a through hole 41 penetrating the main bearing member 23, and has an annular space inside to form a muffler chamber 43 of an inflatable muffler. ing. The peripheral flange of the muffler 35 is fixed to the main bearing member 23 by a bolt 45,
A muffler discharge port 47 is provided on the upper surface.
【００３３】図２，図４，図５は、吐出ポート２７と、
マフラ吐出口４７を設置する位置関係とその形状を具体
的に示したものである。FIGS. 2, 4 and 5 show a discharge port 27,
7 specifically shows a positional relationship and a shape of the muffler discharge port 47.
【００３４】マフラ３５内に励起される周方向の１次共
鳴モードは、例えば、図２に示す如く、吐出ポート２７
からマフラ３５内に冷媒ガスが吐出される際に、マフラ
３５内空間の音響特性により、マフラ形状及び寸法で定
まる数多くの周波数で共鳴が発生するので、それらの周
波数付近では音が増幅され騒音が増大する。The circumferential primary resonance mode excited in the muffler 35 is, for example, as shown in FIG.
When the refrigerant gas is discharged from the muffler 35 into the muffler 35, resonance occurs at a number of frequencies determined by the muffler shape and dimensions due to the acoustic characteristics of the space inside the muffler 35, so that sound is amplified near those frequencies and noise is reduced. Increase.
【００３５】しかしながら、それらの共鳴周波数は、マ
フラ３５内で明確な共鳴モードを持ち、騒音が増幅する
箇所と、騒音がほとんど増幅されない箇所が分布される
形態をとる。それらの箇所は、共鳴周波数により異なっ
てくるが、マフラ３５の形状が単純な円形の場合には、
基準点がほぼシャフト軸心Ｘを通る共鳴の節４９の位置
となり、騒音が増幅されない箇所となる。節４９を挟ん
で吐出ポート２７に位置する部位がプラスで示すモード
の腹となり音圧値が最大となる。一方、周方向１８０度
移動した位置でもマイナスで示す共鳴モードの腹とな
り、音圧値が最大となるため、このマイナスで示す共鳴
モードの腹の領域に、吐出ポート２７から遠く、膨張空
間が長くとれ、しかも効率よく音圧を下げられるマフラ
吐出口４７を１つ配置してある。However, those resonance frequencies have a distinct resonance mode in the muffler 35, and take a form in which a portion where noise is amplified and a portion where noise is hardly amplified are distributed. These locations differ depending on the resonance frequency, but when the shape of the muffler 35 is a simple circle,
The reference point is substantially the position of the resonance node 49 passing through the shaft axis X, and is a place where the noise is not amplified. The portion located at the discharge port 27 across the node 49 becomes the antinode of the mode indicated by plus, and the sound pressure value becomes maximum. On the other hand, even at a position shifted by 180 degrees in the circumferential direction, the antinode of the resonance mode indicated by a minus becomes the antinode, and the sound pressure value becomes maximum. A single muffler discharge port 47 is provided which can reduce the sound pressure efficiently.
【００３６】この場合、共鳴音は、マフラの外周に近づ
くほど音圧値が高くなる所から図４に示す如くマフラ吐
出口４７をマフラ３５の外周に接近ａさせて配置するよ
うにしてもよい。In this case, the muffler discharge port 47 may be arranged closer to the outer periphery of the muffler 35 as shown in FIG. 4 from the place where the sound pressure value increases as the resonance sound approaches the outer periphery of the muffler. .
【００３７】また、図５に示す如く、さらに効率よく吐
出できるようにマフラ吐出口４７を、軸心中心とする長
円の形状にすることも可能である。Further, as shown in FIG. 5, the muffler discharge port 47 can be formed in an elliptical shape with the center of the axis as a center so as to discharge more efficiently.
【００３８】このように構成されたロータリコンプレッ
サ３によれば、圧縮室３３で圧縮された冷媒ガスは、マ
フラ３５内に吐出され、マフラ３５に設けられたマフラ
吐出口４７から密閉ケース１内へ吐出されるようにな
る。According to the rotary compressor 3 configured as described above, the refrigerant gas compressed in the compression chamber 33 is discharged into the muffler 35, and from the muffler discharge port 47 provided in the muffler 35 into the closed case 1. It will be ejected.
【００３９】この動作時において、マフラ３５は、急激
な冷媒ガスの吐出に際して発生する騒音に対し、膨張型
マフラとして作用し、騒音を低減させる。この時、マフ
ラ吐出口４７は、吐出ポート２７から遠く離れた位置で
１つ設けられているため、長い膨張空間が確保され、効
率よく音を弱められる。In this operation, the muffler 35 acts as an expansion type muffler against noise generated when the refrigerant gas is suddenly discharged, thereby reducing the noise. At this time, since one muffler discharge port 47 is provided at a position far away from the discharge port 27, a long expansion space is secured, and the sound can be efficiently reduced.
【００４０】一方、マフラ吐出口４７は、音圧値が高く
なる位置に設けて、圧力を下げることができるため、図
３点線（従来例）から実線（本発明）で示す如く、１．
６ｋＨｚ帯域音や３．１５ｋＨｚ帯域音において大幅な
騒音低減効果（斜線領域）が得られた。On the other hand, since the muffler discharge port 47 can be provided at a position where the sound pressure value becomes high to reduce the pressure, as shown by the dotted line (conventional example) in FIG.
A significant noise reduction effect (shaded area) was obtained in the 6 kHz band sound and the 3.15 kHz band sound.
【００４１】図６，図７はマフラ３５を高さ方向に仕切
って構成される第２の実施形態を示したものである。FIGS. 6 and 7 show a second embodiment in which the muffler 35 is partitioned in the height direction.
【００４２】即ち、吐出ポート２７を有する圧縮機構部
９に、前記吐出ポート２７を覆うと共に圧縮機構部９の
シャフト軸心Ｘを中心とする円形状に形成された上下２
段の第１マフラ３５ａと第２マフラ３５ｂを設け、下位
側となる第１マフラ３５ａの上面に、吐出ポート２７に
対してシャフト軸心Ｘを挟んで周方向に１８０度移動し
た位置に第１マフラのマフラ吐出口４７ａを設ける。上
位側となる第２マフラ３５ｂの上面に、図７矢印の如く
前記第１マフラのマフラ吐出口４７ａから周方向に６０
〜９０度移動した位置に第２マフラのマフラ吐出口４７
ｂを設けるものである。That is, the compression mechanism 9 having the discharge port 27 is provided with a circular upper and lower part 2 covering the discharge port 27 and having a circular shape centered on the shaft axis X of the compression mechanism 9.
The first muffler 35a and the second muffler 35b of the step are provided, and the first muffler 35a on the lower side is located on the upper surface of the first muffler 35a at a position shifted by 180 degrees in the circumferential direction with respect to the discharge port 27 across the shaft axis X. A muffler discharge port 47a for the muffler is provided. On the upper surface of the second muffler 35b on the upper side, as shown by the arrow in FIG.
The muffler discharge port 47 of the second muffler is located at a position shifted by 90 degrees.
b is provided.
【００４３】なお、他の構成要素は第１の実施形態と同
一のため同一符号を付して詳細な説明を省略する。The other components are the same as those in the first embodiment, and therefore, are denoted by the same reference numerals, and detailed description is omitted.
【００４４】かかる第２の実施形態によれば、吐出ポー
ト２７から周方向に１８０度移動した位置にマフラ吐出
口４７ａ設けられた第１マフラ３５ａにより、図３に示
す如く、１．６ｋＨｚや３．１５ｋＨｚ帯域音の騒音低
下が得られる一方、第１マフラ３５ａのマフラ吐出口４
７ａから周方向に６０〜９０度移動した位置にマフラ吐
出口４７ｂが設けられた第２マフラ３５ｂにより、１．
６ｋＨｚや３．１５ｋＨｚ帯域音から外れた周方向の共
鳴周波数帯域の騒音低減が図れる。これにより、広域に
わたる周波数帯域の騒音を低下させることが出来る。According to the second embodiment, as shown in FIG. 3, the first muffler 35a provided with the muffler discharge port 47a at a position shifted by 180 degrees in the circumferential direction from the discharge port 27 allows the 1.6 kHz or 3 kHz .15 kHz band noise, the muffler discharge port 4 of the first muffler 35a.
A second muffler 35b provided with a muffler discharge port 47b at a position shifted 60 to 90 degrees in the circumferential direction from 7a.
The noise can be reduced in the resonance frequency band in the circumferential direction deviating from the 6 kHz or 3.15 kHz band sound. As a result, noise in a wide frequency band can be reduced.
【００４５】図８は、高さ方向の１次共鳴モードの騒音
低減を図った第３の実施形態を示したもので、図におい
て、プラスとマイナスは音圧が最大となる共鳴モードの
腹を示し、点線が音圧が最小となる共鳴モードの節を示
している。FIG. 8 shows a third embodiment in which the noise in the primary resonance mode in the height direction is reduced. In the figure, plus and minus indicate the antinodes of the resonance mode in which the sound pressure becomes maximum. The dotted line indicates the resonance mode node where the sound pressure is minimized.
【００４６】マフラ３５は、マフラ内空間の周方向の共
鳴と同様に、マフラ３５内高さ方向共鳴も騒音（特に、
４ｋＨｚおよび５ｋＨｚ帯域音）の原因となっている。
高さ方向の１次共鳴周波数が密閉ケース１下面の共振周
波数と一致した場合、大きな騒音として放射される。In the muffler 35, the resonance in the height direction inside the muffler 35 as well as the resonance in the circumferential direction of the space inside the muffler 35 is noise (in particular,
(4 kHz and 5 kHz band sounds).
When the primary resonance frequency in the height direction matches the resonance frequency on the lower surface of the closed case 1, it is radiated as loud noise.
【００４７】この対策としてマフラ３５内の高さを低く
し、高さ方向の１次共鳴周波数を、およそ６０００Ｈｚ
以上に設定することが効果的である。６０００Ｈｚ以上
の周波数の振動および騒音は、密閉ケース１内を伝達・
放射されにくく、かつ、人の耳に伝わる騒音となりにく
い。As a countermeasure against this, the height inside the muffler 35 is reduced, and the primary resonance frequency in the height direction is set to about 6000 Hz.
It is effective to set the above. Vibration and noise with a frequency of 6000 Hz or more are transmitted through the closed case 1.
It is hard to be radiated and is hard to generate noise transmitted to human ears.
【００４８】そこで、例えば、冷媒ガスの音速を１９０
ｍ／ｓｅｃとした場合、高さ方向の１次共鳴周波数を６
０００Ｈｚ以上に設定するには、高さＨは下式によって
導き出される。Therefore, for example, the sound velocity of the refrigerant gas is set to 190
m / sec, the primary resonance frequency in the height direction is 6
To set it above 000 Hz, the height H is derived by the following equation.
【００４９】Ｈ≦１９０／６０００／２≒０．０１６ これにより、マフラ３５内空間を１６ｍｍ以下とするこ
とで、図９点線（従来例）から実線（本発明）で示す如
く、高さ方向の１次共鳴周波数となる４ｋＨｚおよび５
ｋＨｚ帯域音の騒音低減（斜線領域）が図れる。H ≦ 190/6000/2 ≒ 0.016 By setting the space inside the muffler 35 to 16 mm or less, as shown by the dotted line (conventional example) in FIG. 4 kHz and 5 as primary resonance frequencies
The noise of the kHz band sound can be reduced (shaded area).
【００５０】図１０と図１１は、高さ方向の１次共鳴周
波数の騒音低減を図るのに、マフラ内を上下２段とした
第４の実施形態を示したものである。FIGS. 10 and 11 show a fourth embodiment in which the muffler has two upper and lower stages in order to reduce the noise at the primary resonance frequency in the height direction.
【００５１】即ち、マフラ内を仕切部材５１により上下
２段に仕切ることで、第１マフラ５３と第２マフラ５５
とを構成するものである。That is, by dividing the inside of the muffler into two upper and lower stages by the partition member 51, the first muffler 53 and the second muffler 55
And
【００５２】第１マフラ５３内の高さ空間は１６ｍｍ以
下に、第２マフラ５５内の高さ空間は１６ｍｍ以下にそ
れぞれ設定されている。The height space in the first muffler 53 is set to 16 mm or less, and the height space in the second muffler 55 is set to 16 mm or less.
【００５３】上下に仕切る仕切部材５１には、第１マフ
ラ５３の１段目のマフラ吐出口５７が、第２マフラ５５
の上面には２段目のマフラ吐出口５９がそれぞれ設けら
れている。A first muffler discharge port 57 of the first muffler 53 has a second muffler 55
Are provided with muffler discharge ports 59 in the second stage.
【００５４】図１１に示すように１段目のマフラ吐出口
５７は、吐出ポート２７に対して１８０度反対側に配置
されている。２段目のマフラ吐出口５９は、１段目のマ
フラ吐出口５７に対して図１１矢印で示す如く周方向に
６０〜９０度移動した位置に配置されている。As shown in FIG. 11, the muffler discharge port 57 of the first stage is disposed 180 ° opposite to the discharge port 27. The second-stage muffler discharge port 59 is disposed at a position shifted by 60 to 90 degrees in the circumferential direction with respect to the first-stage muffler discharge port 57 as shown by an arrow in FIG.
【００５５】なお、他の構成要素については第１の実施
形態と同一のため同一符号を付して詳細な説明を省略す
る。The other components are the same as those in the first embodiment, and therefore, are denoted by the same reference numerals and will not be described in detail.
【００５６】したがって、この第４の実施形態によれ
ば、１段目のマフラ吐出口５７を有する第１マフラ５３
により、図９に示す如く、高さ方向の１次共鳴周波数と
なる４ｋＨｚ及び５ｋＨｚ帯域音の騒音低減（斜線領
域）が図れる。Therefore, according to the fourth embodiment, the first muffler 53 having the first-stage muffler discharge port 57 is provided.
As a result, as shown in FIG. 9, it is possible to reduce the noise (hatched area) of the 4 kHz and 5 kHz band sounds that are the primary resonance frequencies in the height direction.
【００５７】また２段目のマフラ吐出口５９を有する第
２マフラ５５により、４〜５ｋＨｚ帯域音から外れた高
さ方向の１次共鳴周波数帯域の騒音を低減することが出
来る。これにより、広域にわたる周波数帯域での騒音を
低減出来る。The second muffler 55 having the second-stage muffler discharge port 59 can reduce the noise in the primary resonance frequency band in the height direction deviating from the 4 to 5 kHz band sound. Thus, noise in a wide frequency band can be reduced.
【００５８】また、第１，第２マフラ５３，５５は、図
１２に示す如く、仕切部材５１を用いずに、円形状に形
成された第１マフラ６１の外側に、円形状に形成された
第２マフラ６３を組付け、第１マフラ６１の外周縁外面
６１ａと第２マフラ６３の外周縁内面６３ａとを隙間が
ないように密着結合させて、上下２段のマフラを構成す
るようにしてもよい。As shown in FIG. 12, the first and second mufflers 53 and 55 are formed in a circular shape outside the circular first muffler 61 without using the partition member 51. The second muffler 63 is assembled, and the outer peripheral edge outer surface 61a of the first muffler 61 and the outer peripheral edge inner surface 63a of the second muffler 63 are tightly joined so that there is no gap, thereby forming an upper and lower two-stage muffler. Is also good.
【００５９】なお、前記の２段マフラ構成は、上下に設
けられているが、これに限定されるものではなく、ロー
タリコンプレッサの駆動軸が水平に配置されたタイプの
ものにあっては、２段マフラ構成は左右に設けても良
い。The above-mentioned two-stage muffler structure is provided vertically, but is not limited to this. For a type in which the drive shaft of the rotary compressor is horizontally arranged, The step muffler configuration may be provided on the left and right.
【００６０】[0060]
【発明の効果】以上、説明したように、この発明のロー
タリコンプレッサによれば、吐出ポートに対して周方向
に１８０度移動した位置に設けられたマフラ吐出口を有
するマフラにより、周方向の共鳴周波数帯域音の騒音低
減を図ることが出来る。As described above, according to the rotary compressor of the present invention, the resonance in the circumferential direction is achieved by the muffler having the muffler discharge port provided at a position shifted by 180 degrees in the circumferential direction with respect to the discharge port. Noise of frequency band sound can be reduced.
【００６１】また、マフラ内の高さを１６ｍｍ以下とす
ることで、高さ方向の共鳴周波数帯域音の騒音低減を図
ることが出来る。By setting the height inside the muffler to 16 mm or less, it is possible to reduce the noise of the resonance frequency band sound in the height direction.
【図１】この発明にかかるロータリコンプレッサの全体
を示す縦断面図。FIG. 1 is a longitudinal sectional view showing an entire rotary compressor according to the present invention.
【図２】圧縮機構部側の吐出ポートに対するマフラ吐出
口の位置を示した第１の実施形態のマフラの概要平面
図。FIG. 2 is a schematic plan view of the muffler according to the first embodiment, showing a position of a muffler discharge port with respect to a discharge port on a compression mechanism side.
【図３】第１の実施形態による周方向の共鳴周波数帯域
音の騒音効果を示した説明図。FIG. 3 is an explanatory diagram showing a noise effect of a resonance frequency band sound in a circumferential direction according to the first embodiment;
【図４】マフラ吐出口を、マフラ外周縁に寄せた位置に
配置した図２と同様の概要平面図。FIG. 4 is a schematic plan view similar to FIG. 2 in which a muffler discharge port is arranged at a position near an outer peripheral edge of the muffler.
【図５】マフラ吐出口を、長円の形状とした図２と同様
の概要平面図。FIG. 5 is a schematic plan view similar to FIG. 2 in which the muffler discharge port has an oval shape.
【図６】マフラ内を高さ方向に仕切った第２の実施形態
を示したマフラの断面図。FIG. 6 is a sectional view of the muffler showing a second embodiment in which the inside of the muffler is partitioned in the height direction.
【図７】第１マフラのマフラ吐出口と第２マフラのマフ
ラ吐出口の位置関係を示したマフラの概要平面図。FIG. 7 is a schematic plan view of a muffler showing a positional relationship between a muffler discharge port of a first muffler and a muffler discharge port of a second muffler.
【図８】マフラ内の高さを１６ｍｍ以下とした第３の実
施形態を示したマフラの概要説明図。FIG. 8 is a schematic explanatory diagram of a muffler showing a third embodiment in which the height inside the muffler is set to 16 mm or less.
【図９】第３の実施形態による高さ方向の共鳴周波数帯
域音の騒音効果を示した説明図。FIG. 9 is an explanatory diagram showing a noise effect of a resonance frequency band sound in the height direction according to the third embodiment.
【図１０】マフラ内の高さを１６ｍｍ以下とした上下２
段のマフラを示した第４の実施形態の断面図。FIG. 10 shows the upper and lower portions of the muffler having a height of 16 mm or less.
Sectional drawing of 4th Embodiment which showed the muffler of steps.
【図１１】上下２段とした１段目のマフラ吐出口と２段
目のマフラ吐出口の位置関係を示したマフラの概要平面
図。FIG. 11 is a schematic plan view of a muffler showing a positional relationship between a first-stage muffler discharge port having two upper and lower stages and a second-stage muffler discharge port.
【図１２】仕切部材を用いずに上下２段のマフラとした
図１０と同様の断面図。FIG. 12 is a cross-sectional view similar to FIG. 10 in which two upper and lower mufflers are used without using a partition member.
【図１３】周方向の一次共鳴モードを示した説明図。FIG. 13 is an explanatory diagram showing a primary resonance mode in a circumferential direction.
９ 圧縮機構部 ２７ 吐出ポート ３５ マフラ ４７ マフラ吐出口 Ｘ シャフト軸心 9 Compression mechanism 27 Discharge port 35 Muffler 47 Muffler discharge port X Shaft center
Claims (10)
吐出ポートを覆うと共に圧縮機構部のシャフト軸心を中
心とする円形状に形成されたマフラを設置し、そのマフ
ラに、前記吐出ポートに対してシャフト軸心を挟んで周
方向に約１８０度移動した位置にマフラ吐出口を設けた
ことを特徴とするロータリコンプレッサ。A muffler that covers the discharge port and is formed in a circular shape around the axis of the shaft of the compression mechanism is provided in a compression mechanism having a discharge port. A rotary compressor characterized in that a muffler discharge port is provided at a position shifted by about 180 degrees in the circumferential direction with respect to a shaft axis.
フラの外周縁に寄せた位置に設けることを特徴とする請
求項１記載のロータリコンプレッサ。2. The rotary compressor according to claim 1, wherein the muffler discharge port is provided at a position close to an outer peripheral edge of the muffler formed in a circular shape.
状としたことを特徴とする請求項１又は２のいずれかに
記載のロータリコンプレッサ。3. The rotary compressor according to claim 1, wherein the muffler discharge port has an elliptical shape that is long in a circumferential direction.
とする請求項１，２又は３のいずれかに記載のロータリ
コンプレッサ。4. The rotary compressor according to claim 1, wherein one muffler discharge port is provided.
吐出ポートを覆うと共に圧縮機構部のシャフト軸心を中
心とする円形状に形成された第１マフラと第２マフラを
設け、前記第１マフラに、吐出ポートに対してシャフト
軸心を挟んで周方向に約１８０度移動した位置にマフラ
吐出口を設け、第２マフラに、前記第１マフラのマフラ
吐出口から周方向に６０〜９０度移動した位置に第２マ
フラのマフラ吐出口を設けたことを特徴とするロータリ
コンプレッサ。5. A first muffler and a second muffler which are formed in a circular shape around a shaft axis of the compression mechanism portion, the first muffler and the second muffler being provided on the compression mechanism portion having a discharge port. The muffler is provided with a muffler discharge port at a position shifted by about 180 degrees in the circumferential direction with respect to the discharge port with respect to the shaft axis, and the second muffler is provided with a muffler discharge port of 60 to 90 circumferentially from the muffler discharge port of the first muffler. A rotary muffler provided with a muffler discharge port of a second muffler at a position shifted by an angle.
吐出ポートを覆うと共に圧縮機構部のシャフト軸心を中
心とする円形状に形成されたマフラを設置し、このマフ
ラ内空間の高さを約１６ｍｍ以下とすることを特徴とす
るロータリコンプレッサ。6. A muffler, which covers the discharge port and is formed in a circular shape about the axis of the shaft of the compression mechanism, is installed in a compression mechanism having a discharge port, and the height of the muffler internal space is reduced. A rotary compressor characterized in that the diameter is about 16 mm or less.
のマフラ内空間の高さを約１６ｍｍ以下としたことを特
徴とする請求項６記載のロータリコンプレッサ。7. The rotary compressor according to claim 6, wherein the space inside the muffler is partitioned in the height direction, and the height of one space inside the muffler is set to about 16 mm or less.
向に仕切られていることを特徴とする請求項７記載のロ
ータリコンプレッサ。8. The rotary compressor according to claim 7, wherein the muffler internal space is partitioned in a height direction by a partition member.
よる２ピースで構成され、第１マフラの外周縁外面と第
２マフラの外周縁内面とを互いに隙間がないように密着
結合したことを特徴とする請求項７記載のロータリコン
プレッサ。9. The muffler is composed of two pieces of a first muffler and a second muffler, and the outer peripheral surface of the first muffler and the inner peripheral surface of the second muffler are tightly joined to each other without any gap. The rotary compressor according to claim 7, wherein:
２マフラとから構成され、前記第１マフラに、吐出ポー
トに対してシャフト軸心を挟んで周方向に１８０度移動
した位置に吐出口を設け、第２のマフラ吐出口を、前記
第１マフラのマフラ吐出口から周方向に６０〜９０度移
動した位置に配置することを特徴とする請求項６記載の
ロータリコンプレッサ。10. A muffler comprising at least a first muffler and a second muffler, wherein the first muffler has a discharge port at a position shifted 180 degrees in a circumferential direction with respect to a discharge port across a shaft axis. The rotary compressor according to claim 6, wherein the second muffler discharge port is provided at a position shifted from the muffler discharge port of the first muffler by 60 to 90 degrees in a circumferential direction.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10184816A JP2000018184A (en) | 1998-06-30 | 1998-06-30 | Rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10184816A JP2000018184A (en) | 1998-06-30 | 1998-06-30 | Rotary compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2000018184A true JP2000018184A (en) | 2000-01-18 |
| JP2000018184A5 JP2000018184A5 (en) | 2005-08-25 |
Family
ID=16159799
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10184816A Pending JP2000018184A (en) | 1998-06-30 | 1998-06-30 | Rotary compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2000018184A (en) |
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| KR20030051084A (en) * | 2001-12-20 | 2003-06-25 | 주식회사 엘지이아이 | Apparatus for reduce the noise of rotary compressor |
| JP2007016771A (en) * | 2006-03-31 | 2007-01-25 | Sanyo Electric Co Ltd | Rotary compressor |
| JP2007016772A (en) * | 2006-03-31 | 2007-01-25 | Sanyo Electric Co Ltd | Rotary compressor |
| KR100747564B1 (en) * | 2001-02-06 | 2007-08-08 | 엘지전자 주식회사 | structure of muffler in rotary compressor |
| WO2008090777A1 (en) * | 2007-01-24 | 2008-07-31 | Daikin Industries, Ltd. | Rotary compressor |
| JP2012255430A (en) * | 2011-02-07 | 2012-12-27 | Panasonic Corp | Compressor |
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| CN105221433A (en) * | 2015-10-22 | 2016-01-06 | 安徽美芝精密制造有限公司 | Baffler and there is its rotary compressor |
| WO2020123273A1 (en) * | 2018-12-10 | 2020-06-18 | Carrier Corporation | Modular compressor discharge system |
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1998
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100747564B1 (en) * | 2001-02-06 | 2007-08-08 | 엘지전자 주식회사 | structure of muffler in rotary compressor |
| KR20030051084A (en) * | 2001-12-20 | 2003-06-25 | 주식회사 엘지이아이 | Apparatus for reduce the noise of rotary compressor |
| JP2007016771A (en) * | 2006-03-31 | 2007-01-25 | Sanyo Electric Co Ltd | Rotary compressor |
| JP2007016772A (en) * | 2006-03-31 | 2007-01-25 | Sanyo Electric Co Ltd | Rotary compressor |
| EP2107247A4 (en) * | 2007-01-24 | 2014-05-07 | Daikin Ind Ltd | Rotary compressor |
| WO2008090777A1 (en) * | 2007-01-24 | 2008-07-31 | Daikin Industries, Ltd. | Rotary compressor |
| EP2107247A1 (en) * | 2007-01-24 | 2009-10-07 | Daikin Industries, Ltd. | Rotary compressor |
| KR101133300B1 (en) | 2007-01-24 | 2012-04-04 | 다이킨 고교 가부시키가이샤 | Rotary compressor |
| US8282364B2 (en) | 2007-01-24 | 2012-10-09 | Daikin Industries, Ltd. | Rotary compressor having a muffler with a discharge region to discharge compressed gas toward an outer surface of the crankshaft |
| JP2012255430A (en) * | 2011-02-07 | 2012-12-27 | Panasonic Corp | Compressor |
| CN103511283A (en) * | 2013-02-05 | 2014-01-15 | 安徽美芝精密制造有限公司 | Silencer of compressor and compressor provided with same |
| CN103967800A (en) * | 2014-05-19 | 2014-08-06 | 松下·万宝(广州)压缩机有限公司 | Novel dissipative and resistive composite exhaust silencer and compressor with same |
| CN105221433A (en) * | 2015-10-22 | 2016-01-06 | 安徽美芝精密制造有限公司 | Baffler and there is its rotary compressor |
| CN105221433B (en) * | 2015-10-22 | 2017-11-07 | 安徽美芝精密制造有限公司 | Muffler and the rotary compressor with it |
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| US11732716B2 (en) | 2018-12-10 | 2023-08-22 | Carrier Corporation | Modular compressor discharge system |
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