JPH0613872B2 - Horizontal rotary compressor - Google Patents
Horizontal rotary compressorInfo
- Publication number
- JPH0613872B2 JPH0613872B2 JP13105684A JP13105684A JPH0613872B2 JP H0613872 B2 JPH0613872 B2 JP H0613872B2 JP 13105684 A JP13105684 A JP 13105684A JP 13105684 A JP13105684 A JP 13105684A JP H0613872 B2 JPH0613872 B2 JP H0613872B2
- Authority
- JP
- Japan
- Prior art keywords
- oil
- discharge
- chamber
- bearing
- barrier
- 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 - Fee Related
Links
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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
- F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
- F04C29/128—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type of the elastic type, e.g. reed valves
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Description
【発明の詳細な説明】 〔発明の利用分野〕 本発明は、例えば冷蔵庫，空気調和機等の冷凍装置に組
込まれる横形ロータリ式圧縮機に関する。TECHNICAL FIELD The present invention relates to a horizontal rotary compressor incorporated in a refrigerating device such as a refrigerator or an air conditioner.
従来の横形ロータリ式圧縮機の構造と性能上の問題点を
第５図から第１０図で以下説明する。第５図は従来の横
形ロータリ式圧縮機（以下圧縮機と云う）の縦断面図で
あり、ケース１の内部に電動要素２と圧縮要素３が収納
され、下方に油２０が貯溜されている。回転軸４は略水
平に配設され、電動要素２の回転力を圧縮要素３に伝達
し、シリンダ６の内壁を偏心回転するローラ７を駆動す
る。第６図、第７図に示すように、軸方向に設けられた
吸込みパイプ２７を経て、ケース１の外部から直接低圧
ガスを吸込み、ローラ７の回転により圧縮した高圧ガス
を図１に示すサブベアリング９に設けた吐出ポート１５
から、第７図に示す吐出サイレンサ２２の内部に吐出す
る。第５図で吐出ガス２１は吐出ガス穴１８ａ，１８
ｂ，１８ｃを経て、ケース１内部に放出された後、吐出
パイプ１９から冷凍サイクルの高圧側に導かれる。一
方、第６図において、ベーン８はシリンダ内を高圧室２
５と低圧室２４に仕切る機能を有し、回転軸４の回転に
従動して往復運動するので、ベーン８を給油ポンプとし
て利用し、第５図においてメインベアリング５の下方に
テーパー形状の吸入ピース１３を固定し、サブベアリン
グ９の下方にテーパー状の吐出穴１４を設けて、給油ポ
ンプの弁要素を構成して、軸４の内側まで給油してい
る。給油された油２０ａは、軸４に設けられた油穴４ａ
から、回転軸４とメインペアリング、サブベアリング
９，およびローラ７との間を潤滑する。しかし、ローラ
７の内側は油で満たされており、ローラ７とシリンダ６
には軸方向にクリアランスが存在し、更に、前述のよう
にケース１内部は高圧であり、油も高圧側にあるために
一部の油２０ａは第６図に見るように、シリンダ低圧室
２４に洩れ、第５図に示すように吐出ガス２１と共に、
吐出サイレンサ２２の内部に吐出される。このように、
シリンダ６の低圧室２４に洩れた油は、従来から公知の
ように冷却の低下させ、入力をアップさせるなどの問題
点があると共に、次のように騒音に対しても、影響を与
えていることがわかった。第９図に吸込み圧力とある周
波数（Ｘ Hz帯域）の騒音レベルの相関性を示す。これ
により、従来の圧縮機は吸込圧が低下すると、Ｘ Hz帯
域の騒音レベルが変動し、レベルも増大している。この
ような吸込圧力がマイナス３０cmＨｇ程度の圧力条件は
冷凍冷蔵庫などにおいては日常ありうる条件であり、こ
の帯域近辺での変騒音は耳ざわりな音であるので改善す
る必要であった。かかる耳ざわりな音の発生原因を検討
した結果、従来の圧縮機はサブベアリング９の凹所内に
油２０ａが溜っていることがわかった。この状態を第８
Ａ図に示す。これから、従来の圧縮機は冷凍冷蔵庫組込
時などの吸込圧力が低い場合には、サブベアリング９の
凹所内即ち、サブベアリング９とカバー１０とで形成さ
れる吐出サイレンサ２２の内部にかなりの油２０ａが溜
っていることがわかった。この原因は、圧縮比が大きい
場合は、吐出ガス２１の量が少ないため、油を上部の吐
出ガス穴１８ａまで吹き上げることができなく、さら
に、シリンダ６内部の低圧室２４の圧力が低いために、
前述したように、ローラ７とシリンダ６の軸方向のクリ
アランスから洩れる油量が多いためである。第９図にこ
の状態で騒音を測定した結果を実線で示す。このとき、
Ｘ Ｈｚのレベルが大きく、かつ変動していることが確
認できた。そこで、前述のサブベアリング９の一端面を
覆う平板状のカバー１０に油ねき穴２６を設け、この油
ぬき穴２６の位置は、サブベアリング９を示す第８Ｂ図
の点線の位置に対応した位置に設け、これにより油を排
出したが、第９図に破線で示すように、今度は、Ｙ Hz
帯域の騒音が大きくなった。この原因は吐出サイレンサ
２２の内部に油がなくなると、吐出サイレンサ２２の形
状が円筒形状となるために、内部に空洞共鳴が発生する
ためである。第１０図に従来の吐出サイレンサの特性を
測定した結果を示す。図に示すように、Ｙ Hz近辺に消
音量が負すなわち、共鳴点があることが明らかになっ
た。The structure and performance problems of the conventional horizontal rotary compressor will be described below with reference to FIGS. 5 to 10. FIG. 5 is a vertical cross-sectional view of a conventional horizontal rotary compressor (hereinafter referred to as a compressor), in which an electric element 2 and a compression element 3 are housed inside a case 1, and oil 20 is stored below. . The rotary shaft 4 is disposed substantially horizontally, transmits the rotational force of the electric element 2 to the compression element 3, and drives the roller 7 that eccentrically rotates the inner wall of the cylinder 6. As shown in FIGS. 6 and 7, the low pressure gas is directly sucked from the outside of the case 1 through the suction pipe 27 provided in the axial direction, and the high pressure gas compressed by the rotation of the roller 7 is shown in FIG. Discharge port 15 provided on the bearing 9
From the inside to the inside of the discharge silencer 22 shown in FIG. In FIG. 5, the discharge gas 21 is the discharge gas holes 18a, 18
After being discharged to the inside of the case 1 through b and 18c, it is guided from the discharge pipe 19 to the high pressure side of the refrigeration cycle. On the other hand, in FIG. 6, the vane 8 has a high pressure chamber 2 inside the cylinder.
5 has a function of partitioning into the low-pressure chamber 24 and reciprocates following the rotation of the rotary shaft 4. Therefore, the vane 8 is used as an oil supply pump, and a tapered suction piece is provided below the main bearing 5 in FIG. 13 is fixed, and a tapered discharge hole 14 is provided below the sub-bearing 9 to form a valve element of the oil supply pump, and oil is supplied to the inside of the shaft 4. The oil 20a supplied is the oil hole 4a provided in the shaft 4.
Therefore, the rotation shaft 4, the main pairing, the sub bearing 9, and the roller 7 are lubricated. However, the inside of the roller 7 is filled with oil, and the roller 7 and the cylinder 6 are
Has a clearance in the axial direction, and as described above, since the inside of the case 1 has a high pressure and the oil is also on the high pressure side, a part of the oil 20a is, as shown in FIG. Leaks to the discharge gas 21 as shown in FIG.
It is discharged into the discharge silencer 22. in this way,
The oil leaking into the low-pressure chamber 24 of the cylinder 6 has problems such as a decrease in cooling and an increase in input as is well known in the related art, and it also affects noise as follows. I understood it. FIG. 9 shows the correlation between the suction pressure and the noise level at a certain frequency (X Hz band). As a result, in the conventional compressor, when the suction pressure decreases, the noise level in the X Hz band fluctuates and the level also increases. Such a pressure condition that the suction pressure is about -30 cmHg is a condition that can be routinely used in refrigerators and refrigerators, and noise around this band is a jarring noise, so it is necessary to improve it. As a result of investigating the cause of such a harsh sound, it was found that the conventional compressor has oil 20a accumulated in the recess of the sub-bearing 9. This state is the 8th
Shown in FIG. Therefore, in the conventional compressor, when the suction pressure is low, such as when the refrigerator is installed in a refrigerator, a considerable amount of oil is provided inside the recess of the sub bearing 9, that is, inside the discharge silencer 22 formed by the sub bearing 9 and the cover 10. It was found that 20a was accumulated. This is because when the compression ratio is large, the amount of the discharge gas 21 is small, so that the oil cannot be blown up to the discharge gas hole 18a in the upper part, and the pressure in the low pressure chamber 24 inside the cylinder 6 is low. ,
This is because, as described above, a large amount of oil leaks from the axial clearance between the roller 7 and the cylinder 6. FIG. 9 shows a result of measuring the noise in this state by a solid line. At this time,
It was confirmed that the X Hz level was large and fluctuated. Therefore, an oil-draining hole 26 is provided in the plate-shaped cover 10 that covers one end surface of the sub-bearing 9 described above, and the position of the oil-draining hole 26 corresponds to the position of the dotted line in FIG. 8B showing the sub-bearing 9. It was installed at the position and the oil was discharged by this, but this time, as shown by the broken line in FIG.
The noise in the band became loud. This is because when the oil inside the discharge silencer 22 is exhausted, the shape of the discharge silencer 22 becomes a cylindrical shape, so that cavity resonance occurs inside. FIG. 10 shows the results of measuring the characteristics of the conventional discharge silencer. As shown in the figure, it was revealed that the sound-deadening volume was negative near Y Hz, that is, there was a resonance point.
従って、従来の圧縮機は、吐出サイレンサ内に油が溜る
場合は、ある周波数Ｘ Hz帯域の騒音が変動し、かつ大
きくなり、油が溜らない場合は、別の特定周波数のＹ
Hz帯域の騒音が大きくなるという問題点があった。Therefore, in the conventional compressor, when oil is accumulated in the discharge silencer, noise in a certain frequency X Hz band fluctuates and becomes large, and when oil is not accumulated, Y of another specific frequency is used.
There is a problem that noise in the Hz band becomes large.
ベアリングに複数の障壁を設け、空間を形成した特許の
例として米国特許第３１３０９０２号がある。An example of a patent in which a bearing is provided with a plurality of barriers to form a space is U.S. Pat. No. 3,130,902.
本発明の目的は、安価で騒音の低い圧縮機を市場に提供
することにある。An object of the present invention is to provide a low cost and low noise compressor to the market.
従来の圧縮機は吸込圧力が低い場合には、吐出サイレン
サ内に油が溜まり、耳ざわりな変騒音が発生し、吐出サ
イレンサ内に油がない場合には、吐出サイレンサ内部に
空洞共鳴が発生し、特定の周波数が大きくなった。そこ
で、サイレンサ内の油を確実に排出可能な構造とするた
めに、２重円筒状のサイレンサとして、外側のサイレン
サのガス通路を狭く構成し、吐出ガスにより、油を吹き
上げ可能な構造とするとともに、多段サイレンサとし
て、吐出サイレンサの消音特性を高めたものである。In the conventional compressor, when the suction pressure is low, oil accumulates in the discharge silencer, a strange noise is generated, and when there is no oil in the discharge silencer, cavity resonance occurs inside the discharge silencer, The specific frequency has increased. Therefore, in order to make it possible to reliably discharge the oil in the silencer, the gas passage of the outer silencer is narrowly configured as a double cylindrical silencer so that the oil can be blown up by the discharge gas. As a multi-stage silencer, the silencer characteristics of the discharge silencer are enhanced.
以下、本発明の一実施例を第１図〜第４図により説明す
る。第１図は本発明の圧縮機の縦断面図の一部を示した
もので、第２図は本発明のサブベアリングＢ′−Ｂ′断
面図を示したものである。本発明のサブベアリング３１
は、外周リブ３１ａと、軸受ボス３１ｃの間に略円筒状
の障壁３１ｂを設け、軸受ボス３１ｃと該略円筒状の障
壁３１ｂを連結する形状の放射状障壁３１ｄと、略円筒
状の障壁３１ｂと外周リブ３１ａを連結する形状の放射
状障壁３１ｅを設けたものである。更に、サイレンサは
吐出弁１６を収納する第１室３２と第２室３３と第３室
３５から成り、第１室と第２室３３の間は上記障壁３１
ｂに溝３１ｇを設けて連通させ、第２室と、第３室の間
は、長溝３４を設けて連通させるとともに、第１室の吐
出弁１６よりも低い位置に油抜き溝３１ｆを設け、該油
ぬき溝３１ｆは長溝３４を連通させたものである。この
ように構成した本発明の圧縮機の動作を以下に説明する
と、電動要素２の回転により、回動軸４が回転し、ロー
ラ７がシリンダ６の内壁を偏心回転すると、吸入パイプ
（図示せず）から吸込まれた低圧ガスは圧縮されて吐出
ポート１５から吐出サイレンサの第１室３２に吐出され
る。前述したように、この時油２０ａも同時に第１室３
２に吐出される。油２０ａは油ぬきの溝３１ｆから前記
長溝３４に吐き出される。また吐出ガス２１は溝３１ｇ
を経て第２室３３を通過した後、長溝３４を経て第３室
３５に導びかれる。吐出ガス２１は長溝３４を通過する
際に、吐出ガスの流速により油２０ａを吹き上げること
ができるものであり、第１室３２の油は連続的に排出が
可能であり、第３室３５まで吹き上げることが可能であ
る。また、第３図に示すように、カバー３９の前記吐出
サイレンサの第３室３５に連通する位置に油ねきの小穴
３９ａを設けることで、第３室３５の油を速やかに、吐
出サイレンサ外部に排出することができる。第４図は本
発明の圧縮機の従来の圧縮機と同一の条件で運転した騒
音レベルを示す。図に見るように、吸込圧力が低い場合
でも、Ｘ Hzの騒音レベルは大きくなることがなく、吐
出サイレンサ内部の油が排出されていることがわかる。
尚、放射状障壁３１ｄは、吐出サイレンサ３２の内部が
円筒形状であると、円筒方向に空洞共鳴が発生すること
があり、これを防止するための障壁であるので、該放射
状障壁３１ｄがない場合でも、吐出サイレンサ内の油を
排出する本発明の機能には何ら影響しない。更に、本実
施例は、サブベアリングに吐出弁１６を装着した例につ
いて説明したが、メインベアリング５側に吐出弁１６を
装着した場合にも、メインベアリングを同様な構造とで
きるので、同様な効果がある。An embodiment of the present invention will be described below with reference to FIGS. FIG. 1 shows a part of a vertical sectional view of a compressor of the present invention, and FIG. 2 shows a sectional view of a sub-bearing B'-B 'of the present invention. Sub-bearing 31 of the present invention
A substantially cylindrical barrier 31b is provided between the outer peripheral rib 31a and the bearing boss 31c, and a radial barrier 31d having a shape connecting the bearing boss 31c and the substantially cylindrical barrier 31b, and a substantially cylindrical barrier 31b. A radial barrier 31e having a shape connecting the outer peripheral ribs 31a is provided. Further, the silencer is composed of a first chamber 32, a second chamber 33 and a third chamber 35 which house the discharge valve 16, and the barrier 31 is provided between the first chamber and the second chamber 33.
The groove 31g is provided in b for communication, the long groove 34 is provided for communication between the second chamber and the third chamber, and the oil drain groove 31f is provided at a position lower than the discharge valve 16 of the first chamber. The oil drain groove 31f is formed by communicating the long groove 34. The operation of the compressor of the present invention configured as described above will be described below. When the rotating shaft 4 is rotated by the rotation of the electric element 2 and the roller 7 eccentrically rotates the inner wall of the cylinder 6, the suction pipe (not shown) is shown. The low-pressure gas sucked from (1) is compressed and discharged from the discharge port 15 to the first chamber 32 of the discharge silencer. As described above, at this time, the oil 20a also simultaneously flows into the first chamber 3
2 is discharged. The oil 20a is discharged into the long groove 34 from the oil-free groove 31f. Further, the discharge gas 21 has a groove 31g.
Then, after passing through the second chamber 33 through the above, it is guided to the third chamber 35 through the long groove 34. When the discharge gas 21 passes through the long groove 34, the oil 20a can be blown up by the flow velocity of the discharge gas, and the oil in the first chamber 32 can be continuously discharged, and blown up to the third chamber 35. It is possible. Further, as shown in FIG. 3, by providing a small hole 39a for oiling in a position of the cover 39 which communicates with the third chamber 35 of the discharge silencer, the oil in the third chamber 35 is promptly discharged to the outside of the discharge silencer. Can be discharged to. FIG. 4 shows the noise level of the compressor of the present invention operated under the same conditions as the conventional compressor. As can be seen from the figure, even when the suction pressure is low, the noise level at X Hz does not increase, and the oil inside the discharge silencer is discharged.
It should be noted that the radial barrier 31d may be a barrier for preventing a cavity resonance in the cylindrical direction when the discharge silencer 32 has a cylindrical shape, and therefore, even if the radial barrier 31d is not present, the radial barrier 31d is a barrier. , The function of the present invention for discharging the oil in the discharge silencer is not affected at all. Further, although the present embodiment has described the example in which the discharge valve 16 is attached to the sub-bearing, even when the discharge valve 16 is attached to the main bearing 5 side, the main bearing can have the same structure, so that the same effect can be obtained. There is.
本発明によれば、吐出サイレンサ内部の油を確実に排出
できるために、吐出弁が油の中で作動することに起因す
る耳障りな音と、油挙動が不安定に変動することと同期
した耳障りな変動音の発生を防止することができる。更
には、吐出弁が油の中で作動することによる弁の開き遅
れ、閉じ遅れなど、圧縮機の入力をアップさせ、冷力を
低下させる要因も改善可能である。これらの機能は部品
点数を増加させることなく構成が可能であり、例えば、
サブベアリングを焼結金属で型形成すれば、容易に本発
明の形状を実現できるため、圧縮機のコストをほとんど
アップすることなく、騒音低減が可能である。よっつ本
発明の実用上の効果は大きい。According to the present invention, since the oil inside the discharge silencer can be reliably discharged, the jarring noise caused by the discharge valve operating in the oil and the jarring noise synchronized with the unstable fluctuation of the oil behavior are produced. It is possible to prevent various fluctuating sounds. Further, it is possible to improve the factors that increase the input of the compressor and reduce the cooling power, such as the delay in opening and closing of the valve due to the operation of the discharge valve in oil. These functions can be configured without increasing the number of parts.
Since the shape of the present invention can be easily realized by molding the sub-bearing with a sintered metal, noise can be reduced with almost no increase in the cost of the compressor. Therefore, the practical effect of the present invention is great.
第１図は本発明の圧縮機の縦断面図、第２図は第１図の
Ｂ′−Ｂ′断面図、第３図は第１図のＣ−Ｃ断面図、第
４図は吸入圧力とある特定周波数の騒音レベルの関係、
第５図は従来の圧縮機の縦断面図、第６図は第５図のＡ
−Ａ断面図、第７図は第５図のＢ−Ｂ断面図、第８Ａ，
８Ｂ図は第５図の運転時の様子を観察した結果、第９図
は第８Ａ、８Ｂ図の騒音測定結果、第１０図は従来の吐
出サイレンサの特性である。 １……ケース、２……電動要素、３……圧縮要素、 ４……回転軸、４ａ……油穴、５……メインベアリン
グ、６……シリンダ、７……ローラ、８……ベーン、９
……サブベアリング、９ａ……外周リブ、９ｂ……軸受
ボス、１０……カバー、１１……給油パイプ、１２……
スプリング、１３……吸入ピース、１４……テーパー状
の吐出穴、１５……吐出ポート、１６……吐出弁、 １７……リテーナ、１８ａ……吐出ガス穴、 １８ｂ……吐出ガス穴、１８ｃ……吐出ガス穴、 １９……吐出パイプ、２０……油、２０ａ……給油され
た油、２１……吐出ガス、２２……吐出サイレンサ、２
３……固定ボルト、２４……低圧室、２５……高圧室、
２６……油抜き穴、３１……本発明のサブベアリング、
３１ａ……外周リブ、３１ｂ……円筒状障壁、 ３１ｃ……軸受ボス、３１ｄ……放射状障壁、 ３１ｅ……放射状障壁、３１ｆ……油抜き溝、 ３１ｇ……溝、３２……第１室、３３……第２室、 ３４……長溝、３５……第３室、３９……カバー、３９
ａ……油抜き穴。1 is a longitudinal sectional view of the compressor of the present invention, FIG. 2 is a sectional view taken along the line B′-B ′ of FIG. 1, FIG. 3 is a sectional view taken along the line CC of FIG. 1, and FIG. 4 is a suction pressure. The relationship between the noise level of a certain specific frequency,
FIG. 5 is a longitudinal sectional view of a conventional compressor, and FIG. 6 is A of FIG.
-A sectional view, FIG. 7 is a BB sectional view of FIG. 5, 8A,
FIG. 8B is a result of observing the operation state of FIG. 5, FIG. 9 is a noise measurement result of FIGS. 8A and 8B, and FIG. 10 is a characteristic of the conventional discharge silencer. 1 ... Case, 2 ... Electric element, 3 ... Compression element, 4 ... Rotating shaft, 4a ... Oil hole, 5 ... Main bearing, 6 ... Cylinder, 7 ... Roller, 8 ... Vane, 9
...... Sub-bearing, 9a …… Outer peripheral rib, 9b …… Bearing boss, 10 …… Cover, 11 …… Oil supply pipe, 12 ……
Spring, 13 ... Suction piece, 14 ... Tapered discharge hole, 15 ... Discharge port, 16 ... Discharge valve, 17 ... Retainer, 18a ... Discharge gas hole, 18b ... Discharge gas hole, 18c ... ... Discharge gas hole, 19 ... Discharge pipe, 20 ... Oil, 20a ... Oiled oil, 21 ... Discharge gas, 22 ... Discharge silencer, 2
3 ... Fixing bolt, 24 ... Low pressure chamber, 25 ... High pressure chamber,
26 ... Oil drain hole, 31 ... Sub-bearing of the present invention,
31a ... Outer peripheral rib, 31b ... Cylindrical barrier, 31c ... Bearing boss, 31d ... Radial barrier, 31e ... Radial barrier, 31f ... Oil drain groove, 31g ... Groove, 32 ... First chamber, 33 ... second chamber, 34 ... long groove, 35 ... third chamber, 39 ... cover, 39
a ... Oil drain hole.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 村田 充 栃木県下都賀郡大平町大字富田800 株式 会社日立製作所栃木工場内 (72)発明者 紺野 元 栃木県下都賀郡大平町大字富田800 株式 会社日立製作所栃木工場内 (56)参考文献 特開 昭56−54987（ＪＰ，Ａ) 特開 昭60−62676（ＪＰ，Ａ) 実開 昭53−97709（ＪＰ，Ｕ) 実開 昭50−48205（ＪＰ，Ｕ) ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Mitsuru Murata 800 Tomita, Ohira-machi, Shimotsuga-gun, Tochigi Hitachi Co., Ltd. Tochigi factory (72) Inventor Gen Konno 800 Tomita, Ohira-machi, Shimotsuga-gun, Tochigi Hitachi Co., Ltd. In Tochigi Plant (56) Reference JP-A-56-54987 (JP, A) JP-A-60-62676 (JP, A) Actual opening Sho-53-97709 (JP, U) Actual opening 50-48205 (JP, A) U)
Claims (2)
グに外周リブと軸受ボスを設けるとともに、両者の間に
略円筒状の障壁を設け、複数の円筒状の部屋を構成し、
該円筒状障壁と軸受ボスの間の部屋に吐出弁を収納し、
しかも吐出弁の下方の円筒状障壁の一部に油抜き溝を設
けたことを特特徴とする横形ロータリ式圧縮機。1. A horizontal rotary compressor, wherein a bearing is provided with an outer peripheral rib and a bearing boss, and a substantially cylindrical barrier is provided between them to form a plurality of cylindrical chambers.
A discharge valve is housed in the chamber between the cylindrical barrier and the bearing boss,
Moreover, the horizontal rotary compressor is characterized in that an oil drain groove is provided in a part of the cylindrical barrier below the discharge valve.
状の部屋は、両者を連結する形状の障壁により複数に分
割されるとともに、複数の部屋は、長溝で連通され、該
長溝に上記円筒状障壁の一部に設けた油抜き溝を連通さ
せたことを特徴とする特許請求の範囲第１項記載の横形
ロータリ式圧縮機。2. The cylindrical chamber surrounded by the cylindrical barrier and the outer peripheral rib is divided into a plurality of chambers by a barrier having a shape connecting the two, and the plurality of chambers are communicated with each other by a long groove, and the chamber is connected to the long groove. The horizontal rotary compressor according to claim 1, wherein an oil drain groove provided in a part of the cylindrical barrier is made to communicate with each other.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13105684A JPH0613872B2 (en) | 1984-06-27 | 1984-06-27 | Horizontal rotary compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13105684A JPH0613872B2 (en) | 1984-06-27 | 1984-06-27 | Horizontal rotary compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6111493A JPS6111493A (en) | 1986-01-18 |
| JPH0613872B2 true JPH0613872B2 (en) | 1994-02-23 |
Family
ID=15048978
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13105684A Expired - Fee Related JPH0613872B2 (en) | 1984-06-27 | 1984-06-27 | Horizontal rotary compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0613872B2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106932481B (en) * | 2017-03-16 | 2023-06-16 | 中国东方电气集团有限公司 | Muffler noise reduction characteristic test system |
| CN111255807B (en) * | 2018-11-30 | 2021-10-19 | 安徽美芝精密制造有限公司 | Bearing for rotary compressor and rotary compressor |
-
1984
- 1984-06-27 JP JP13105684A patent/JPH0613872B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6111493A (en) | 1986-01-18 |
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