JPS6056195A - Rotary compressor - Google Patents

Abstract

PURPOSE:To improve the efficiency by compressor while considering resonant muffler effect, by coupling an arched expansion chamber and a linear valve chamber in acute angle and eliminating a small path communicating between the expansion chamber and valve chamber thereby reducing the pressure loss of delivery refrigerant. CONSTITUTION:A linear recess 17 for mounting a valve and an arched recess 18 having an opening 18a near the central portion 17b of said recess 17 are made in the counter-cylinder face 16a of bearing 16 where they 17, 18 are communicated such that the center lines L, L' will cross with acute angle at the opening 18a while separated by a partitioner 19 from a delivery chamber in delivery cover 20. Refrigerant in the cylinder is delivered to the recess 17, 18 and muffled through expansion muffler effect while the opening 18a near the central portion 17b will cause resonant muffler effect in linear direction at the recess 17 to improve muffler effect and to deliver the refrigerant through a hole 21 in the partitioner 19 into the delivery chamber.

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.

従来例の構成とその問題点 冷凍冷蔵装置に用いられる回転型圧縮機は、シリンダ内
で圧縮された冷媒の圧力変動により太きな騒音を発生す
る。そのため、従来より消音器を軸受は等に設は騒音低
減を図る方法がとられていたが・効率の低下を生じる等
の問題点があった。Conventional Structure and Problems Rotary compressors used in freezing and refrigerating systems generate loud noises due to pressure fluctuations of refrigerant compressed within the cylinder. For this reason, conventional methods have been used to reduce noise by installing silencers on bearings, etc., but there have been problems such as a decrease in efficiency.

第１図ケ参照しながら従来の構成について説明する。The conventional configuration will be explained with reference to FIG.

図において、１は回転型圧縮機で、２は密閉ケース、３
はステータで、密閉ケース２に焼バメ固足されている。In the figure, 1 is a rotary compressor, 2 is a closed case, and 3 is a rotary compressor.
is a stator, which is firmly attached to the sealed case 2 by shrink fitting.

４はロータで、クランクシャフト５と連結されている。A rotor 4 is connected to a crankshaft 5.

６はピストンで、７はシリンダである。８はロータ側の
軸受で、冨閉ケース２に溶接固定されてｂる。９はシャ
フト端部の軸受で、軸受９の反シリンダ面９ａ［は、バ
ルブ１０ａの装着用の凹部１０及び小溝１１により凹部
１０と連通する凹陥部１２が設けである。ｉ　ｏｂはバ
ルブ孔である。１３は軸受９とカップ状の吐出カバー１
４間に介在された仕切板である。この仕切板１３により
、これらの凹部１０．凹陥部１２及び小溝１１ば、それ
ぞれ、バルブ室１０ｃ。6 is a piston, and 7 is a cylinder. 8 is a bearing on the rotor side, which is fixed to the closed case 2 by welding. Reference numeral 9 denotes a bearing at the end of the shaft, and the anti-cylinder surface 9a of the bearing 9 is provided with a recess 10 for mounting a valve 10a and a recess 12 communicating with the recess 10 through a small groove 11. i ob is a valve hole. 13 is a bearing 9 and a cup-shaped discharge cover 1
This is a partition plate interposed between the four. This partition plate 13 allows these recesses 10. The concave portion 12 and the small groove 11 each form a valve chamber 10c.

膨張室１２ａ、バルブ室１０ｃと膨張室１２ａを連通さ
せる小通路１１ａ、及び吐出カバー１４と仕切阪１３で
形成される吐出チャンバー１４ａを形成する。また仕切
板１３には凹陥部１２と対応する位置に、膨張室１２’
ａと吐出チャンバー１４ａを連通ずる孔１５が設けられ
ている。An expansion chamber 12a, a small passage 11a that communicates the valve chamber 10c and the expansion chamber 12a, and a discharge chamber 14a formed by the discharge cover 14 and the partition wall 13 are formed. Further, the partition plate 13 has an expansion chamber 12' at a position corresponding to the concave portion 12.
A hole 15 is provided to communicate the discharge chamber 14a with the discharge chamber 14a.

かかる構成において、シリンダ７内で圧縮された冷媒は
バルブ孔１ｏｂより、パルプ室１０ｃに吐出される。さ
らに、冷媒は小通路１１ａより、膨張室１２ａに噴出さ
れ、小孔１５より吐出チャンバー１４ａ内に吐出され、
吐出チャンバー１４ａより密閉ケース２内に放出させる
。このように、シリンダ７内で圧縮される冷媒は、吐出
チャ／バー１０を経て密閉ケース２内に放出される前に
膨張室１２ａｆＩ：通過する。従って、シリンダγ内で
発生した冷媒の圧力変動成分はバルブ室１ｏや膨張室１
２ａを冷媒が通過する際に膨張型消音効果により減衰さ
れるため、密閉ケース２内に放射される冷媒の圧力脈動
成分は減少し、圧縮機騒音は減少する。In this configuration, the refrigerant compressed within the cylinder 7 is discharged from the valve hole 1ob into the pulp chamber 10c. Furthermore, the refrigerant is ejected from the small passage 11a into the expansion chamber 12a, and is discharged from the small hole 15 into the discharge chamber 14a,
It is discharged into the sealed case 2 from the discharge chamber 14a. In this way, the refrigerant compressed within the cylinder 7 passes through the expansion chamber 12afI before being discharged into the closed case 2 via the discharge chamber/bar 10. Therefore, the pressure fluctuation component of the refrigerant generated in the cylinder γ is reflected in the valve chamber 1o and expansion chamber 1.
When the refrigerant passes through 2a, it is attenuated by the expansion type silencing effect, so the pressure pulsation component of the refrigerant radiated into the closed case 2 is reduced, and the compressor noise is reduced.

しかし、このような方法では、パルプ室１００と膨張室
１２ａ間の通路１１ａで冷媒の圧力損失が生じるため、
圧縮機効率の低下をもたらすという問題があった。However, in such a method, pressure loss of the refrigerant occurs in the passage 11a between the pulp chamber 100 and the expansion chamber 12a.
There was a problem that this resulted in a decrease in compressor efficiency.

発明の目的 本発明は、軸受等に設けられた消音器形状を圧力損失が
少なく、かつ消音効果が十分得られるものとし、圧縮機
の効率向上を図ることを目的とする。OBJECTS OF THE INVENTION It is an object of the present invention to improve the efficiency of a compressor by using a shape of a muffler provided in a bearing etc. to have a shape that causes less pressure loss and provides a sufficient muffling effect.

発明の構成 この目的勿達成するため、本発明は軸受の反シリンダ面
に直線状のバルブ装着用の凹部とこの凹部の中央部付近
に連通用開口部を位［置せしめ、かつ鋭角で凹部と交わ
る円弧状の凹陥部全役け、前記凹陥部と対応した孔を有
する仕切板を前記軸受と吐出チャンバーとの間に介する
ことにより、膨張型消音器を構成し、冷媒ガスが直線状
の凹部から円孤状の凹陥部に流れる際に圧力ロスを減じ
、また凹部での共鳴の節部放射による消音効果を加味し
て圧縮機の効率向上を図るものである。Structure of the Invention In order to achieve this object, the present invention includes a linear valve mounting recess on the anti-cylinder surface of the bearing, a communication opening near the center of this recess, and an acute angle between the recess and the recess. An expansion type muffler is constructed by intersecting arc-shaped recesses and a partition plate having holes corresponding to the recesses between the bearing and the discharge chamber, and the refrigerant gas flows through the linear recess. This aims to improve the efficiency of the compressor by reducing the pressure loss when flowing from the to the arc-shaped concave part, and also by taking into account the silencing effect due to the nodal radiation of the resonance in the concave part.

実施例の説明 以下、第４図〜第６図を参照しながら、本発明の一実施
例について詳細に説明する。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て説
明を省略する。DESCRIPTION OF EMBODIMENTS An embodiment of the present invention will be described in detail below with reference to FIGS. 4 to 6. Incidentally, in order 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.

１６はクランクシャフト５ケ軸支する軸受で、軸受１６
の反シリンダ面１６ａには、バルブ１７ａ？収納装着す
る凹部１７及び、この凹部１７の中央部１７ｂ付近に開
口部１８ａを有する円弧状の凹陥部１８が設けである。16 is a bearing that supports five crankshafts, bearing 16
On the opposite cylinder surface 16a, there is a valve 17a? A recess 17 for storing and mounting, and an arc-shaped recess 18 having an opening 18a near the center 17b of the recess 17 are provided.

前記凹部１７と凹陥部１８は開口部１８ａにおいて、各
々の中心線（力。The recessed portion 17 and the recessed portion 18 are located at the respective center lines (forces) at the opening 18a.

（２“）が鋭角で交差するように鋭角に交わっている。(2") intersect at an acute angle.

１７ｃはバルブ孔である。１９は軸受１６とカップ状の
吐出カバー２０間に介在された仕切板である。この仕切
板１９により、これらの凹部１７、凹陥部１８は、互い
に開口部１８ａにて連通したバルブ室１７ｄ、室１８ｂ
、及び吐出カバー２０と仕切板１９で形成される吐出チ
ャンバー２０　ａ金形成している。17c is a valve hole. Reference numeral 19 denotes a partition plate interposed between the bearing 16 and the cup-shaped discharge cover 20. The partition plate 19 allows the recess 17 and the recess 18 to form a valve chamber 17d and a chamber 18b that communicate with each other through the opening 18a.
, and the discharge chamber 20a formed by the discharge cover 20 and the partition plate 19 is made of gold.

また仕切板１９７こは凹陥部１８と対応して、室１８ｂ
の吐出チャンバー２０　ａを連通ずる孔２１が設けられ
ている。Furthermore, the partition plate 197 corresponds to the recessed portion 18, and the partition plate 197 corresponds to the chamber 18b.
A hole 21 is provided that communicates with the discharge chamber 20a.

かかる構成において、シリンダＹ内で圧縮された／＠媒
はバルブ孔１７ｃより、パルプ室１７ｄに吐出される。In this configuration, the /@ medium compressed within the cylinder Y is discharged from the valve hole 17c into the pulp chamber 17d.

さらに冷媒は、開１−」部１８ａより室ｉ　ｓｂｌ経て
、小孔２１より吐出チャンバー２０ａ内に吐出され、吐
出チャンバー２０ａより密閉ケース２２内に放出される
。Further, the refrigerant is discharged from the opening 18a through the chamber isbl, from the small hole 21 into the discharge chamber 20a, and from the discharge chamber 20a into the closed case 22.

従って、シリンダ７内で発生した冷媒の圧力変動成分は
、パルプ室１７ｄ及び室１８ｂ釦冷媒が通過する靜に膨
張型消音効果により減衰される。Therefore, the pressure fluctuation component of the refrigerant generated in the cylinder 7 is attenuated by the expansion type silencing effect as the refrigerant passes through the pulp chamber 17d and the button chamber 18b.

又室１８ｂの開口部１８ａはパルプ室１７ｂの中央部１
７ｂ付近に設けたため、パルプ室１７ｂの直線方間の共
鳴型消音効果が強く現れ、しかも中央部１７ｂ付近開口
による＋ｉｉＪ記共鳴の室１８ｂに対する節郡位］ｄで
の放射による消音効果により圧力変動成分は減衰される
。Further, the opening 18a of the chamber 18b is located at the central portion 1 of the pulp chamber 17b.
7b, the resonance type silencing effect in the straight direction of the pulp chamber 17b appears strongly, and the pressure fluctuation is caused by the silencing effect due to the radiation at +iiJ resonance chamber 18b due to the opening near the central portion 17b. components are attenuated.

このように、膨張型消音効果の他に、共鳴型消音効果及
び共鳴の節部位−での放射による消音効果が得られるた
め開口部１８ａでしぼり部が設けられていないにもかか
わらず、シリンダ７内で発生した圧力変動成分は十分に
減衰され、そのため密閉ケース内に放射される冷媒の圧
力変動成分は減少し圧縮機騒音は減少する。In this way, in addition to the expansion-type silencing effect, the resonance-type silencing effect and the silencing effect due to radiation at the resonance node site can be obtained. The pressure fluctuation component generated inside the compressor is sufficiently attenuated, so the pressure fluctuation component of the refrigerant radiated into the closed case is reduced, and compressor noise is reduced.

さらにパルプ室１７ｄと室１８ｂ間にしぼり部が存在せ
ず、かつ画室は鋭角で交わるため、開口部１８ａにおけ
る圧力損失はほとんどなく、圧縮機の効率向上が図れる
。Further, since there is no constriction between the pulp chamber 17d and the chamber 18b, and the compartments intersect at an acute angle, there is almost no pressure loss at the opening 18a, improving the efficiency 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全
収納する回転型圧縮機を有し、反シリンダ面に形１戊さ
れた直線状のバルブ装着用の凹部と、この四部の中央部
付近に形成した開口部において鋭角で凹部と交わる円孤
状の凹陥部を倚する軸受と、凹陥部を有する面側に配置
される吐出チャ／バーと前記軸受と前記吐出チャンバー
の間に介され、かつ前記凹陥部に対応して開孔した孔を
有する仕切板と勿備えることにより、密閉ケース内に放
射されるシリンダ内で発生した圧力変動成分を膨張型消
音効果と共鳴型消音効果と、この節部位置での放則によ
る消音効果とにより減衰することができ、かつ圧縮機の
効率をおだやかな凹部と凹陥部の連接により、圧力損失
の発生〒防止しほとんど低下させることなく騒音低減勿
図ることができるものである。Effects of the Invention As described above, the present invention has a rotary compressor in which all electric compression elements are housed in a sealed case, and a rectilinear valve mounting recess formed on the opposite side of the cylinder, and four parts of the rotary compressor. between the bearing and the discharge chamber, a bearing that holds a circular arc-shaped recess that intersects with the recess at an acute angle in an opening formed near the center of the bearing, and a discharge chamber/bar disposed on the side having the recess; By providing a partition plate having a hole corresponding to the concave portion, the pressure fluctuation component generated in the cylinder that is radiated into the sealed case can be suppressed by an expansion type noise reduction effect and a resonance type noise reduction effect. The noise can be attenuated by the noise reduction effect and the noise reduction effect due to the radiation at the joint position, and the connection between the recesses and the recesses, which calms the efficiency of the compressor, prevents the generation of pressure loss and reduces noise with almost no reduction in the efficiency of the compressor. Of course, this can be reduced.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図は従来例の回転型圧縮機の断面図、第２図は、ベ
アリング、仕切板、吐出カバー紫示す分解斜視図、第３
図は第１図のＩＩＩ−ＩＩＩ’線における断面図、第４
図は本発明の一実施例を示す回転型圧縮機の断面図、第
５図はベアリング、仕切板、吐出カバーで示す分解斜視
図、第６図は第４図の■−ｖｉ“ｉ腺における断面図で
ある。 ７・・・・・シリンダ、１６・・・・・・軸受、１７・
・・・・凹部、１８・・・・凹陥部、１９・・・・・・
仕ψＪ板、２ｏ・・・・吐出カバー、２１・・・・・孔
。 代理人の氏名　弁３浬士　中　尾　敏　男　ほか１名第
１図 第２図 ｆ（ｃＬ ＠３図 ２ Ｏｂ１０ 第４図 ■ 第５図 第６図Figure 1 is a sectional view of a conventional rotary compressor, Figure 2 is an exploded perspective view of the bearing, partition plate, and discharge cover shown in purple.
The figure is a cross-sectional view taken along the line III-III' in Figure 1.
The figure is a sectional view of a rotary compressor showing an embodiment of the present invention, FIG. 5 is an exploded perspective view showing the bearing, partition plate, and discharge cover, and FIG. 6 is the It is a sectional view. 7... Cylinder, 16... Bearing, 17...
... recess, 18 ... recess, 19 ...
Part ψJ plate, 2o...Discharge cover, 21...hole. Name of agent: Toshio Nakao, 3rd grade Bencher, and 1 other person Figure 1 Figure 2 f (cL @3 Figure 2 Ob10 Figure 4 ■ Figure 5 Figure 6

Claims (1)

【特許請求の範囲】[Claims] 電動圧縮要素を収納した密閉ケースと、反シリンダ面に
形成された直線状のバルブ装着用の凹部と、この凹部の
中央部付近に連通開口部を位置せしめ、かつ、鋭角で前
記凹部と交わる円弧状の凹陥部を有する軸受と、前記凹
陥部を有する面側に配置される吐出チャンバーと、前記
軸受と前記吐出チャンバーの間に介在され、かつ前記凹
陥部に対応して開孔した孔を有する仕切板とを備えた回
転型圧縮機。A sealed case housing an electric compression element, a linear valve mounting recess formed on the opposite side of the cylinder, and a circle having a communication opening located near the center of the recess and intersecting the recess at an acute angle. A bearing having an arcuate concave portion, a discharge chamber disposed on the side having the concave portion, and a hole interposed between the bearing and the discharge chamber and opened corresponding to the concave portion. A rotary compressor equipped with a partition plate.