JP4897867B2 - Multi-cylinder rotary compressor and manufacturing method thereof - Google Patents
Multi-cylinder rotary compressor and manufacturing method thereof Download PDFInfo
- Publication number
- JP4897867B2 JP4897867B2 JP2009264973A JP2009264973A JP4897867B2 JP 4897867 B2 JP4897867 B2 JP 4897867B2 JP 2009264973 A JP2009264973 A JP 2009264973A JP 2009264973 A JP2009264973 A JP 2009264973A JP 4897867 B2 JP4897867 B2 JP 4897867B2
- Authority
- JP
- Japan
- Prior art keywords
- cylinder
- divided
- plate
- crankshaft
- thickness
- 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
Landscapes
- Applications Or Details Of Rotary Compressors (AREA)
Description
この発明は，多シリンダロータリ圧縮機及びその製造方法に関するものである。 The present invention relates to a multi-cylinder rotary compressor and a manufacturing method thereof.
従来，多シリンダロータリ圧縮機として，特許文献１に示すものがあった。この多シリンダロータリ圧縮機は，電動要素（モータ）と複数個の回転圧縮要素（第１及び第２の回転圧縮要素）を密閉容器に収納し，電動要素と複数個の回転圧縮要素を偏心部を有するクランクシャフトで連結している。そして，回転圧縮要素の間に介在する仕切板は２枚の分割板から成り，分割板に設けられた通し孔にクランクシャフトを挿通した状態で組立を行い，しかるのち２枚の分割板の外周を溶接等によって溶着固定する。上記特許文献１の回転式圧縮機によれば，仕切板が２枚に分割されており，分割面に微小な隙間が存在したとしても，仕切板外周を溶着固定することにより微小な隙間からの冷媒漏れを抑制し，性能低下の無い多シリンダロータリ圧縮機を容易に提供できる。 Conventionally, there has been a multi-cylinder rotary compressor shown in Patent Document 1. The multi-cylinder rotary compressor stores an electric element (motor) and a plurality of rotary compression elements (first and second rotary compression elements) in a hermetic container, and the electric element and the plurality of rotary compression elements are arranged in an eccentric portion. Are connected by a crankshaft having The partition plate interposed between the rotary compression elements is composed of two divided plates, and the assembly is performed with the crankshaft inserted into the through holes provided in the divided plates, and then the outer periphery of the two divided plates. Is fixed by welding or the like. According to the rotary compressor of Patent Document 1, the partition plate is divided into two pieces, and even if there is a minute gap on the divided surface, the outer periphery of the partition plate is fixed by welding and fixing. It is possible to easily provide a multi-cylinder rotary compressor that suppresses refrigerant leakage and has no performance degradation.
従来，多シリンダロータリ圧縮機の構造において仕切板を複数に分割した場合，仕切板の接合部間の微小な隙間から冷媒漏れが生じることが性能低下の原因と考えられており，上記特許文献1においては，接合部を溶接等により溶着固定し微小な隙間からの冷媒漏れを低減する技術が説明されている。
しかしながら，２枚の分割板に板厚差がある場合において，上記の方法により微小な隙間を塞いだとしても，シリンダ内を低圧部と高圧部に分けるベーンの高さ方向の隙間からの冷媒漏れによる性能低下が生じる場合があり，問題となっていた。
Conventionally, when the partition plate is divided into a plurality of parts in the structure of the multi-cylinder rotary compressor, refrigerant leakage is considered to be caused by a minute gap between the joint portions of the partition plate. Describes a technique for reducing the leakage of refrigerant from a minute gap by welding and fixing a joint portion by welding or the like.
However, when there is a difference in thickness between the two split plates, even if a minute gap is closed by the above method, refrigerant leakage from the gap in the height direction of the vane that divides the inside of the cylinder into a low pressure portion and a high pressure portion. Performance degradation may occur due to the problem.
この発明は，前記のような問題を解決するためになされたもので，圧縮機構部を組立てた際にベーンの高さ方向の隙間からの冷媒漏れによる性能低下を抑制することができる小型大容量の多シリンダロータリ圧縮機及びその製造方法を提供することを目的とするものである。 The present invention has been made to solve the above-described problems, and has a small size and large capacity capable of suppressing performance degradation due to refrigerant leakage from the gap in the height direction of the vane when the compression mechanism is assembled. It is an object of the present invention to provide a multi-cylinder rotary compressor and a manufacturing method thereof.
この発明に係わる多シリンダロータリ圧縮機は，密閉容器内にモータ及び圧縮機構部を備え，上記圧縮機構部は，軸方向に離間して配置された複数個の偏心部と，これらの偏心部の間に位置する中間部とを有し，上記モータにより駆動されるクランクシャフト，上記複数個の偏心部外周に対応して配置された複数個のシリンダ，上記クランクシャフトの軸受を有し，上記シリンダを挟むように上記クランクシャフトの軸方向両端部に設置された枠体，上記クランクシャフトの中間部に挿入され，上記複数個のシリンダ間を仕切る仕切板，及び上記クランクシャフトの偏心部外周に回転自在に取り付けられたローラを備え，上記ローラ，上記シリンダ，上記枠体，及び上記仕切板で囲まれる空間を圧縮室として形成すると共に，上記ローラと摺動するように上記シリンダに保持されたベーンにより，上記圧縮室を低圧部と高圧部に分ける多シリンダロータリ圧縮機において，上記仕切板はその径方向の中心線に沿って分割された２つの分割板で構成され，上記ベーンに接する側の分割板の板厚が他方の分割板の板厚より大きく設定されたものである。 A multi-cylinder rotary compressor according to the present invention includes a motor and a compression mechanism in a hermetic container, and the compression mechanism includes a plurality of eccentric parts arranged apart from each other in the axial direction, and the eccentric parts. A crankshaft driven by the motor, a plurality of cylinders arranged corresponding to the outer periphery of the plurality of eccentric parts, and a bearing for the crankshaft. Frames installed at both ends in the axial direction of the crankshaft so as to sandwich the crankshaft, inserted into an intermediate part of the crankshaft, and rotated around the eccentric part of the crankshaft, and a partition plate for partitioning the plurality of cylinders A freely attached roller is formed, and a space surrounded by the roller, the cylinder, the frame, and the partition plate is formed as a compression chamber, and the roller and the slide are formed. In a multi-cylinder rotary compressor that divides the compression chamber into a low pressure portion and a high pressure portion by vanes held in the cylinder, the partition plate is divided into two divided plates along the radial center line. The thickness of the divided plate on the side in contact with the vane is set larger than the thickness of the other divided plate.
この発明に係わる多シリンダロータリ圧縮機の製造方法は，密閉容器内にモータ及び圧縮機構部を備え，上記圧縮機構部は，軸方向に離間して配置された複数個の偏心部と，これらの偏心部の間に位置する中間部とを有し，上記モータにより駆動されるクランクシャフト，上記複数個の偏心部外周に対応して配置された複数個のシリンダ，上記クランクシャフトの軸受を有し，上記シリンダを挟むように上記クランクシャフトの軸方向両端部に設置された枠体，上記クランクシャフトの中間部に挿入され，上記複数個のシリンダ間を仕切る仕切板，及び上記クランクシャフトの偏心部外周に回転自在に取り付けられたローラを備え，上記ローラ，上記シリンダ，上記枠体，及び上記仕切板で囲まれる空間を圧縮室として形成すると共に，上記ローラと摺動するように上記シリンダに保持されたベーンにより，上記圧縮室を低圧部と高圧部に分けると共に，上記仕切板はその径方向の中心線に沿って分割された２つの分割板で構成され，上記ベーンに接する側の分割板の板厚が他方の分割板の板厚より大きく設定された多シリンダロータリ圧縮機の製造方法において，上記分割板の板厚をそれぞれ測定して保管する工程と，上記保管された分割板を組立に用いる場合，上記ベーンに接する側の分割板の板厚が他方の分割板の板厚より大きくなるように選択する工程と，上記選択された分割板を上記シリンダ，及び上記枠体と締結する工程とを含むものである。 A manufacturing method of a multi-cylinder rotary compressor according to the present invention includes a motor and a compression mechanism section in a sealed container, and the compression mechanism section includes a plurality of eccentric parts arranged apart from each other in the axial direction. A crankshaft driven by the motor, a plurality of cylinders arranged corresponding to the outer circumferences of the eccentric parts, and a bearing for the crankshaft. , Frames installed at both axial ends of the crankshaft so as to sandwich the cylinder, a partition plate inserted into the intermediate portion of the crankshaft to partition the plurality of cylinders, and an eccentric portion of the crankshaft A roller rotatably attached to an outer periphery, and a space surrounded by the roller, the cylinder, the frame, and the partition plate is formed as a compression chamber; The compression chamber is divided into a low pressure portion and a high pressure portion by vanes held in the cylinder so as to slide with the roller, and the partition plate is divided into two divided plates along the radial center line. In the method of manufacturing a multi-cylinder rotary compressor, in which the thickness of the split plate on the side in contact with the vane is set larger than the thickness of the other split plate, the thickness of each of the split plates is measured and stored. And, when the stored divided plate is used for assembly, the step of selecting the divided plate on the side in contact with the vane to be larger than the thickness of the other divided plate, and the selected divided plate And a step of fastening the plate to the cylinder and the frame.
この発明は，圧縮機構部を組立てた際にベーンの高さ方向の隙間が小さくなり，ベーンの高さ方向の隙間からの冷媒漏れによる性能低下を抑制することができる小型大容量の多シリンダロータリ圧縮機を容易に得ることができる。 According to the present invention, when the compression mechanism portion is assembled, the gap in the height direction of the vane becomes small, and a small and large-capacity multi-cylinder rotary that can suppress performance degradation due to refrigerant leakage from the gap in the height direction of the vane. A compressor can be obtained easily.
実施の形態１．
以下，この発明の実施の形態１による多シリンダロータリ圧縮機について図を参照して説明する。本実施の形態１では，圧縮室を２室有する２シリンダ式の冷凍・空調機用ロータリ圧縮機を例に挙げて説明する。
図１は実施の形態１の多シリンダロータリ圧縮機の縦断面図であり，図２は図１におけるＡ−Ａ線の断面図，図３は図１におけるＢ−Ｂ線の断面図，図４は仕切板の斜視図を示す。
Embodiment 1 FIG.
A multi-cylinder rotary compressor according to Embodiment 1 of the present invention will be described below with reference to the drawings. In the first embodiment, a two-cylinder rotary compressor for a refrigeration / air conditioner having two compression chambers will be described as an example.
1 is a longitudinal sectional view of a multi-cylinder rotary compressor according to Embodiment 1, FIG. 2 is a sectional view taken along line AA in FIG. 1, FIG. 3 is a sectional view taken along line BB in FIG. Shows a perspective view of the partition plate.
本実施の形態の多シリンダロータリ圧縮機１００は，密閉容器であるシェル１０１と，シェル１０１の内部に設置された駆動源であるモータ１０２と，同じくシェル１０１の内部に設置された圧縮機構部１０３を備える。シェル１０１は，上部シェル１０１ａと中間シェル１０１ｂと下部シェル１０１ｃを有する。上部シェル１０１ａは，外部からモータ１０２に電力を供給するためのガラス端子１０４と，圧縮された冷媒を圧縮機外部へ吐出する吐出パイプ１０５が設けられている。中間シェル１０１ｂは，モータ１０２と圧縮機構部１０３が固定されており，圧縮機構部１０３へ冷媒を導く吸入パイプ１０６が固定されている。吸入パイプ１０６は，吸入マフラ１０７に接続されており，吸入マフラ１０７内で冷媒の気液分離，及び冷媒中のゴミの除去が行われる。 The multi-cylinder rotary compressor 100 of the present embodiment includes a shell 101 that is a hermetic container, a motor 102 that is a drive source installed inside the shell 101, and a compression mechanism unit 103 that is also installed inside the shell 101. Is provided. The shell 101 includes an upper shell 101a, an intermediate shell 101b, and a lower shell 101c. The upper shell 101a is provided with a glass terminal 104 for supplying electric power to the motor 102 from the outside, and a discharge pipe 105 for discharging the compressed refrigerant to the outside of the compressor. The intermediate shell 101 b has a motor 102 and a compression mechanism 103 fixed thereto, and a suction pipe 106 that guides the refrigerant to the compression mechanism 103 is fixed. The suction pipe 106 is connected to a suction muffler 107, and gas-liquid separation of the refrigerant and removal of dust in the refrigerant are performed in the suction muffler 107.
モータ１０２は，固定子１０２ａと回転子１０２ｂを有しており，回転子１０２ｂはクランクシャフト１０８に取り付けられている。モータ１０２で発生した回転トルクはクランクシャフト１０８を通して圧縮機構部１０３に伝達される。
圧縮機構部１０３は，クランクシャフト１０８，第１軸受１０９ａが内周部に形成された第１枠体１０９，第１シリンダ１１０，第１バネ１１１，第１ベーン１１２，第１ローラ１１３，仕切板１１４，第２シリンダ１１５，第２軸受１１６ａが内周部に形成された第２枠体１１６，第２バネ１１７，第２ベーン１１８，第２ローラ１１９を有している。
クランクシャフト１０８は，ロータ嵌合部１２０，第１軸受挿入部１２１，第１偏心部１２２，中間部１２３，第２偏心部１２４，第２軸受挿入部１２５を有している。第１偏心部１２２と第２偏心部１２４は離間して配置され，中間部１２３はこれらの偏心部の間に位置している。第１偏心部１２２と第２偏心部１２４は，偏心位相が１８０度異なっており，それぞれの外周面には第１ローラ１１３と第２ローラ１１９が回転自在に取り付けられる。
The motor 102 has a stator 102a and a rotor 102b, and the rotor 102b is attached to the crankshaft 108. The rotational torque generated by the motor 102 is transmitted to the compression mechanism unit 103 through the crankshaft 108.
The compression mechanism 103 includes a crankshaft 108, a first frame 109 having a first bearing 109a formed on the inner periphery, a first cylinder 110, a first spring 111, a first vane 112, a first roller 113, and a partition plate. 114, a second cylinder 115, a second bearing 116a, a second frame 116 formed on the inner periphery, a second spring 117, a second vane 118, and a second roller 119.
The crankshaft 108 includes a rotor fitting portion 120, a first bearing insertion portion 121, a first eccentric portion 122, an intermediate portion 123, a second eccentric portion 124, and a second bearing insertion portion 125. The first eccentric part 122 and the second eccentric part 124 are spaced from each other, and the intermediate part 123 is located between these eccentric parts. The first eccentric portion 122 and the second eccentric portion 124 have an eccentric phase that is 180 degrees different, and the first roller 113 and the second roller 119 are rotatably attached to the outer peripheral surfaces of the first eccentric portion 122 and the second eccentric portion 124, respectively.
第１枠体１０９の下端面，第１シリンダ１１０の内周面，仕切板１１４の上端面，及び第１ローラ１１３の外周面で囲まれる空間が第１圧縮室１２６となる。仕切板１１４の下端面，第２シリンダ１１５の内周面，第２枠体１１６の上端面，及び第２ローラ１１９の外周面で囲まれる空間が第２圧縮室１２７となる。第１シリンダ１１０及び第２シリンダ１１５には径方向に伸縮する第１バネ１１１及び第２バネ１１７が取り付けられており，各バネの押付け力により第１ベーン１１２及び第２ベーン１１８が第１ローラ１１３及び第２ローラ１１９の外周面に押付けられる。第１ベーン１１２及び第２ベーン１１８は第１圧縮室１２６及び第２圧縮室１２７を低圧部１２８と高圧部１２９に分ける機能を持つ。本例では，第１ベーン１１２と第２ベーン１１８の位相は等しい。 A space surrounded by the lower end surface of the first frame 109, the inner peripheral surface of the first cylinder 110, the upper end surface of the partition plate 114, and the outer peripheral surface of the first roller 113 becomes the first compression chamber 126. A space surrounded by the lower end surface of the partition plate 114, the inner peripheral surface of the second cylinder 115, the upper end surface of the second frame 116, and the outer peripheral surface of the second roller 119 is a second compression chamber 127. A first spring 111 and a second spring 117 that expand and contract in the radial direction are attached to the first cylinder 110 and the second cylinder 115, and the first vane 112 and the second vane 118 are moved to the first roller by the pressing force of each spring. 113 and the outer peripheral surface of the second roller 119. The first vane 112 and the second vane 118 have a function of dividing the first compression chamber 126 and the second compression chamber 127 into a low pressure part 128 and a high pressure part 129. In this example, the phases of the first vane 112 and the second vane 118 are equal.
図４に示すように，仕切板１１４は，その径方向の中心線に沿って分割された第１分割板１３０及び第２分割板１３１を組み合わせることにより構成される。ベーン１１２，１１８に接する側を第1分割板，もう一方の側を第２分割板とし，第1分割板１３０の板厚は第２分割板１３１の板厚よりわずかに大きい。第１分割板１３０は，上端面１３０ａ，下端面１３０ｂ，分割面１３０ｃ，及び外周面１３０ｄの４つの面を有する。分割面１３０ｃにはクランクシャフト１０８挿入用の溝１３０eがある。第２分割板１３１は，上端面１３１ａ，下端面１３１ｂ，分割面１３１ｃ，及び外周面１３１ｄの４つの面を有する。分割面１３１ｃにはクランクシャフト１０８挿入用の溝１３１eがある。第１分割板１３０及び第２分割板１３１には圧縮機構部１０３の組立に用いられるボルト締結用の通し穴１３０f及び１３１fが複数個（本例ではそれぞれ３個ずつ）設けられている。 As shown in FIG. 4, the partition plate 114 is configured by combining a first divided plate 130 and a second divided plate 131 that are divided along the radial center line. The side that contacts the vanes 112 and 118 is the first divided plate, and the other side is the second divided plate. The thickness of the first divided plate 130 is slightly larger than the thickness of the second divided plate 131. The first divided plate 130 has four surfaces: an upper end surface 130a, a lower end surface 130b, a divided surface 130c, and an outer peripheral surface 130d. The dividing surface 130c has a groove 130e for inserting the crankshaft 108. The second divided plate 131 has four surfaces: an upper end surface 131a, a lower end surface 131b, a divided surface 131c, and an outer peripheral surface 131d. The dividing surface 131c has a groove 131e for inserting the crankshaft 108. The first divided plate 130 and the second divided plate 131 are provided with a plurality of bolt fastening holes 130f and 131f (three each in this example) used for assembling the compression mechanism 103.
第１分割板１３０及び第２分割板１３１は，分割面１３０ｃ及び分割面１３１ｃが接触するように組立てられる。このとき，第１仕切板１３０の溝１３０ｄと第２仕切板１３１の溝１３１ｄが向かい合わせとなり，クランクシャフト挿入穴１３２を形成する。クランクシャフト挿入孔１３２の径はクランクシャフト１０８の中間部１２３の径より大きく，第１偏心部１２２及び第２偏心部１２４の径より小さい。このような構造であるため，クランクシャフト１０８の偏心部の偏心量が大きいものであっても，クランクシャフト挿入孔１３２の径を小さくすることができ，クランクシャフト挿入孔１３２からの漏れを少なくすることができる。 The first divided plate 130 and the second divided plate 131 are assembled so that the divided surface 130c and the divided surface 131c are in contact with each other. At this time, the groove 130d of the first partition plate 130 and the groove 131d of the second partition plate 131 face each other to form a crankshaft insertion hole 132. The diameter of the crankshaft insertion hole 132 is larger than the diameter of the intermediate portion 123 of the crankshaft 108 and smaller than the diameters of the first eccentric portion 122 and the second eccentric portion 124. Because of such a structure, even if the eccentric amount of the eccentric portion of the crankshaft 108 is large, the diameter of the crankshaft insertion hole 132 can be reduced, and leakage from the crankshaft insertion hole 132 is reduced. be able to.
本実施の形態の多シリンダロータリ圧縮機１００は，ガラス端子部１０５からの通電によりシェル１０１内部に設置されたモータ１０２を駆動して，第１偏心部１２２及び第２偏心部１２４を有するクランクシャフト１０８を回転させる。そして，吸入マフラ１０７及び吸入パイプ１０６を通じて，冷媒は，第１シリンダ１１０，第１ベーン１１２及び第１ローラ１１３により形成される第１圧縮室１２６，並びに第２シリンダ１１５，第２ベーン１１８及び第２ローラ１１９により形成される第２圧縮室１２７に吸入され，クランクシャフト１０８の回転に伴って圧縮され，一定の圧力になると吐出口１３３からシェル１０１内部へ吐出され，吐出パイプ１０５より圧縮機外部へ吐出される。 A multi-cylinder rotary compressor 100 according to the present embodiment drives a motor 102 installed in a shell 101 by energization from a glass terminal portion 105 to have a first eccentric portion 122 and a second eccentric portion 124. 108 is rotated. Then, through the suction muffler 107 and the suction pipe 106, the refrigerant passes through the first compression chamber 126 formed by the first cylinder 110, the first vane 112, and the first roller 113, and the second cylinder 115, the second vane 118, and the first. The air is sucked into the second compression chamber 127 formed by the two rollers 119, compressed as the crankshaft 108 rotates, and discharged to the inside of the shell 101 from the discharge port 133 when a constant pressure is reached. Is discharged.
ここで第１分割板１３０と第２分割板１３１の板厚に微小な差がある場合に生じる隙間について，下記に説明する。一般的に異なる２つの部品を組合わせた場合，それらの板厚には必ず微小な差が生じるが，圧縮機構部１０３のような気密性を必要とする機構において，わずかな隙間が性能を低下させる要因となる。 Here, the gap generated when there is a minute difference in the thickness of the first divided plate 130 and the second divided plate 131 will be described below. In general, when two different parts are combined, there will always be a slight difference in their thickness, but in a mechanism that requires airtightness such as the compression mechanism 103, a slight gap will degrade the performance. It becomes a factor to make.
第１分割板１３０の板厚が第２分割板１３１の板厚よりわずかに大きい場合をケース１，第１分割板１３０の板厚が第２分割板１３１の板厚よりわずかに薄い場合をケース２として，以下説明する。
ケース１について図５に圧縮機構部１０３の縦断面図を示す。第１分割板１３０の上側には第１バネ１１１と第１ベーン１１２が設置されており，第１分割板１３０の下側には第２バネ１１７と第２ベーン１１８が設置されている。第１分割板１３０と第２分割板１３１から構成される仕切板１１４を第１シリンダ１１０と第２シリンダ１１５で上下から挟み込んだ場合，第１分割板１３０の板厚が第２分割板１３１の板厚よりわずかに大きいため，第１分割板１３０と第１シリンダ１１０，及び第２シリンダ１１５が密着するのに対し，第２分割板１３１と第１シリンダ１１０，及び第２シリンダ１１５の間には微小な隙間が生じる。
Case 1 when the thickness of the first divided plate 130 is slightly larger than the thickness of the second divided plate 131, Case 1 when the thickness of the first divided plate 130 is slightly thinner than the thickness of the second divided plate 131 2 will be described below.
FIG. 5 shows a longitudinal sectional view of the compression mechanism 103 for the case 1. A first spring 111 and a first vane 112 are installed on the upper side of the first divided plate 130, and a second spring 117 and a second vane 118 are installed on the lower side of the first divided plate 130. When the partition plate 114 composed of the first divided plate 130 and the second divided plate 131 is sandwiched from above and below by the first cylinder 110 and the second cylinder 115, the thickness of the first divided plate 130 is equal to that of the second divided plate 131. Since it is slightly larger than the plate thickness, the first divided plate 130 and the first cylinder 110 and the second cylinder 115 are in close contact with each other, whereas the second divided plate 131 and the first cylinder 110 and the second cylinder 115 are interposed between them. Produces a minute gap.
一方ケース２について，図６に圧縮機構部１０３の縦断面図を示す。この場合，第２分割板１３１と第１シリンダ１１０，及び第２シリンダ１１５が密着し，第１分割板１３０と第１シリンダ１１０，及び第２シリンダ１１５間に微小な隙間が生じる。第１分割板１３０側にはベーン１１２，１１８が設けられているため，第１分割板１３０と第１シリンダ１１０，及び第２シリンダ１１５間の隙間分だけ，ベーン高さ方向の隙間が増大する。 On the other hand, FIG. 6 shows a longitudinal sectional view of the compression mechanism 103 for the case 2. In this case, the second divided plate 131, the first cylinder 110, and the second cylinder 115 are in close contact with each other, and a minute gap is generated between the first divided plate 130, the first cylinder 110, and the second cylinder 115. Since the vanes 112 and 118 are provided on the first divided plate 130 side, the gap in the vane height direction is increased by the gap between the first divided plate 130 and the first cylinder 110 and the second cylinder 115. .
図７にケース１とケース２について，それぞれベーン１１２により高圧部１２８と低圧部１２９が仕切られている様子を示す。ベーン高さをu，シリンダ高さをs，第１分割板１３０と第２分割板１３１の接合面の段差をtとすると，ケース１の場合は図７(a)のようにベーン高さ方向の隙間はs-uとなり，ケース２の場合は図７(b)のようにs+t-uとなる。圧縮機構部１０３の組立において，ベーン１１２とシリンダ１１０，１１５は，ベーン高さ方向の隙間が必要最小限となるように管理されており，ケース２のように圧縮機構部１０３を組立てた後にベーン高さ方向の隙間が増大すると，シリンダ１１０，１１５内の高圧部１２８から低圧部１２９へ冷媒漏れが生じ，性能が低下する。 FIG. 7 shows the case 1 and the case 2 in which the high pressure part 128 and the low pressure part 129 are partitioned by the vane 112, respectively. When the vane height is u, the cylinder height is s, and the level difference between the joining surfaces of the first divided plate 130 and the second divided plate 131 is t, in case 1, the vane height direction is as shown in FIG. In the case 2, the gap is s + tu as shown in FIG. 7 (b). In assembling the compression mechanism portion 103, the vane 112 and the cylinders 110 and 115 are managed so that a gap in the vane height direction is minimized, and the vane 112 is assembled after the compression mechanism portion 103 is assembled as in the case 2. When the gap in the height direction increases, refrigerant leakage occurs from the high pressure portion 128 in the cylinders 110 and 115 to the low pressure portion 129, and the performance is degraded.
ここでシリンダ１１０，１１５と仕切板１１４間の隙間から冷媒漏れが生じる場合と，ベーン高さ方向の隙間から冷媒漏れが生じる場合を比較すると，シリンダ１１０，１１５と仕切板１１４間の隙間の連通長さがベーン高さ方向の隙間の連通長さよりも長いため，シリンダ１１０，１１５と仕切板１１４間の隙間からの冷媒漏れによる性能低下よりベーン高さ方向の隙間からの冷媒漏れによる性能低下の方が大きい。 Here, comparing the case where the refrigerant leaks from the gap between the cylinders 110 and 115 and the partition plate 114 and the case where the refrigerant leaks from the gap in the vane height direction, the communication of the gap between the cylinders 110 and 115 and the partition plate 114 is compared. Since the length is longer than the communication length of the gap in the vane height direction, the performance deterioration due to the refrigerant leakage from the gap in the vane height direction is lower than the performance deterioration due to the refrigerant leakage from the gap between the cylinders 110, 115 and the partition plate 114. Is bigger.
図８(a)(b)に第１分割板１３０と第２分割板１３１の接合面に段差tが生じた場合，第１シリンダ１１０，及び第１枠体１０９の第１軸受１０９ａが傾く様子を示す。シリンダ１１０が傾くとシリンダ１１０とローラ１１３の隙間が変化し，第１軸受１０９ａが傾くとクランクシャフト１０８と第１軸受１０９ａの隙間が変化するが，第１軸受１０９ａの方が仕切板１１４から距離があるため，第１軸受１０９ａとクランクシャフト１０８の隙間の変化の方がシリンダ１１０とローラ１１３の隙間の変化より大きく，性能や信頼性への影響が大きい。 8 (a) and 8 (b), when a step t occurs on the joint surface between the first divided plate 130 and the second divided plate 131, the first cylinder 109 and the first bearing 109a of the first frame 109 are inclined. Indicates. When the cylinder 110 is tilted, the gap between the cylinder 110 and the roller 113 changes. When the first bearing 109a is tilted, the gap between the crankshaft 108 and the first bearing 109a changes, but the first bearing 109a is farther from the partition plate 114. Therefore, the change in the gap between the first bearing 109a and the crankshaft 108 is larger than the change in the gap between the cylinder 110 and the roller 113, and the influence on performance and reliability is great.
第１軸受クリアランスc，第１枠体高さh，シリンダ高さs，第２分割板１３１の幅r，クランクシャフト半径dとすると，第１軸受の微小な傾きqについて，近似式(１)，(２)が成り立つ。
r・q=t (１)
√{(h+s)２+d２}・q=c (２)
よって，式(3)が成り立つ。
t/r = c/√{(h+s)２+d２} (３)
第１軸受１０９ａがクランクシャフト１０８に接触するくらい傾いた場合，第１軸受１０９ａが磨耗し信頼性が著しく低下することから，段差tは式(４)を満たす値とすることで信頼性を確保することができる。
t<c・r/√{(h+s)２+d２} (４)
Assuming that the first bearing clearance c, the first frame height h, the cylinder height s, the width r of the second divided plate 131, and the crankshaft radius d, an approximate expression (1), (2) holds.
r · q = t (1)
√ {(h + s) 2 + d 2 } · q = c (2)
Therefore, Equation (3) holds.
t / r = c / √ {(h + s) 2 + d 2 } (3)
When the first bearing 109a is tilted so as to contact the crankshaft 108, the first bearing 109a is worn and the reliability is remarkably lowered. Therefore, the reliability is ensured by setting the step t to a value satisfying the equation (4). can do.
t <c ・ r / √ {(h + s) 2 + d 2 } (4)
ここで段差tが式(４)を満たす上限程度である１0μmの場合において，ケース１では性能低下が生じないが，ケース２では性能低下が生じることから，第１分割板１３０と第２分割板１３１の板厚の差が１0μm以下であり，第１分割板１３０の板厚が第２分割板１３１の板厚より大きいことにより，性能低下のない多シリンダロータリ圧縮機を実現することができる。 Here, in the case where the step t is about 10 μm, which is the upper limit satisfying the expression (4), the performance is not deteriorated in the case 1 but the performance is deteriorated in the case 2, so that the first divided plate 130 and the second divided plate are Since the difference in plate thickness of 131 is 10 μm or less and the plate thickness of the first divided plate 130 is larger than the plate thickness of the second divided plate 131, a multi-cylinder rotary compressor without performance degradation can be realized.
以上のように本実施の形態１によれば，複数個のシリンダを有するロータリ圧縮機において，各シリンダの間を仕切る仕切板が２つに分割され，それらの板厚に微小な差が生じた場合でも，ベーンに接する側の分割板の板厚をもう一方の側の分割板の板厚よりわずかに大きくすることにより，ベーン高さ方向の隙間からの冷媒漏れを抑制し，性能低下の無い多シリンダロータリ圧縮機を実現することができる。 As described above, according to the first embodiment, in the rotary compressor having a plurality of cylinders, the partition plates for partitioning the cylinders are divided into two parts, and there is a slight difference in the plate thicknesses. Even in this case, by making the thickness of the split plate on the side in contact with the vane slightly larger than the thickness of the split plate on the other side, refrigerant leakage from the gap in the vane height direction is suppressed, and there is no degradation in performance. A multi-cylinder rotary compressor can be realized.
実施の形態２．
次に，この発明の実施の形態２による多シリンダロータリ圧縮機の圧縮機構部１０３の製造方法について説明する。本実施の形態２で説明する多シリンダロータリ圧縮機は，実施の形態１で説明した多シリンダロータリ圧縮機と同様の構成とし，実施の形態２で説明する部品番号は実施の形態１と同じものを用いる。
仕切板１１４を構成する第１分割板１３０と第２分割板１３１は加工が終了した後，それぞれ板厚を測定し，5μmごとに区分して保管する。圧縮機構部１０３の部品を選択する際に，第１分割板１３０を選択後，第１分割板１３０より１区分薄い区分から第２分割板１３１を１枚選択する。これらの２枚の分割板を１組として扱う。
Embodiment 2. FIG.
Next, a method for manufacturing the compression mechanism 103 of the multi-cylinder rotary compressor according to Embodiment 2 of the present invention will be described. The multi-cylinder rotary compressor described in the second embodiment has the same configuration as the multi-cylinder rotary compressor described in the first embodiment, and the part numbers described in the second embodiment are the same as those in the first embodiment. Is used.
After the processing of the first divided plate 130 and the second divided plate 131 constituting the partition plate 114 is finished, the plate thickness is measured, and is divided and stored every 5 μm. When selecting the components of the compression mechanism 103, after selecting the first divided plate 130, one second divided plate 131 is selected from the sections that are one section thinner than the first divided plate 130. These two divided plates are treated as one set.
次に，圧縮機構部１０３の組立工程の手順を図９に示したフローチャートを基に説明する。
ステップ１では，クランクシャフト１０８の第１軸受挿入部１２１に対する第１偏心部１２２に第1ローラ１１３を取り付けた状態の偏心量を測定する。
ステップ２では，クランクシャフト１０８の第２軸受挿入部１２５に対する第２偏心部１２４に第２ローラ１１９を取り付けた状態の偏心量を測定する。
ステップ３では，第１シリンダ１１０と第１軸受１０９ａを有する第１枠体１０９を，上記偏心量の測定結果を基にクランクシャフト１０８が回転した場合に第１ローラ１１３外周と第１シリンダ１１０内周の隙間が最適となるように組立てる。本例では，第１シリンダ１１０と第１枠体１０９にはそれぞれ６個のボルト穴が設けられており，ステップ３ではそのうち各３個のボルト穴にボルトを挿入して第１シリンダ１１０と第１枠体１０９を固定する。
ステップ４では，第２シリンダ１１５と第２軸受１１６ａを有する第２枠体１１６を，上記偏心量の測定結果を基にクランクシャフト１０８が回転した場合に第２ローラ１１９外周と第２シリンダ１１５内周の隙間が最適となるように組立てる。本例では，第２シリンダ１１５と第２枠体１１６にはそれぞれ６個のボルト穴が設けられており，ステップ４ではそのうち各３個のボルト穴にボルトを挿入して第２シリンダ１１５と第２枠体１１６を固定する。
ステップ５では，上記ステップ３により第１枠体１０９を固定した第１シリンダ１１０に第１ベーン１１２と第１ローラ１１３を挿入する。
ステップ６では，クランクシャフト１０８を第１ローラ１１３，及び第１シリンダ１１０と第１枠体１０９の第１軸受１０９ａに挿入する。
Next, the procedure of the assembly process of the compression mechanism unit 103 will be described based on the flowchart shown in FIG.
In step 1, the amount of eccentricity in a state where the first roller 113 is attached to the first eccentric portion 122 with respect to the first bearing insertion portion 121 of the crankshaft 108 is measured.
In step 2, the amount of eccentricity in a state where the second roller 119 is attached to the second eccentric portion 124 with respect to the second bearing insertion portion 125 of the crankshaft 108 is measured.
In step 3, the first frame 109 having the first cylinder 110 and the first bearing 109a is moved between the outer periphery of the first roller 113 and the first cylinder 110 when the crankshaft 108 is rotated based on the measurement result of the eccentricity. Assemble so that the circumferential clearance is optimal. In this example, each of the first cylinder 110 and the first frame 109 is provided with six bolt holes. In step 3, bolts are inserted into the three bolt holes, and the first cylinder 110 and the first frame 109 are inserted. One frame 109 is fixed.
In step 4, when the crankshaft 108 rotates on the second frame 116 having the second cylinder 115 and the second bearing 116 a based on the measurement result of the eccentricity, Assemble so that the circumferential clearance is optimal. In this example, each of the second cylinder 115 and the second frame 116 is provided with six bolt holes. In step 4, bolts are inserted into the three bolt holes, and the second cylinder 115 and the second frame 116 are connected. The two-frame body 116 is fixed.
In step 5, the first vane 112 and the first roller 113 are inserted into the first cylinder 110 to which the first frame 109 is fixed in step 3.
In step 6, the crankshaft 108 is inserted into the first roller 113, the first cylinder 110, and the first bearing 109 a of the first frame 109.
ステップ７では，第１分割板１３０と第２分割板１３１を第１シリンダ１１０上に設置する。このとき，板厚を測定して保管された分割板から第１分割板１３０を選択後，第１分割板１３０より１区分薄い区分から第２分割板１３１を１枚選択し，これらの２枚の分割板を１組の仕切板１１４として扱う。
そして，クランクシャフト１０８の中間部１２３が第１分割板１３０及び第２分割板１３１で形成されるクランクシャフト挿入穴１３２を通るように，第１分割板１３０の分割面１３０ｃと第２分割板１３１の分割面１３１ｃを合わせる。
ステップ８では，仕切板１１４の内周中心と第１シリンダ１１０内周中心が一致するように仕切板１１４の位置決めを行う。
ステップ９では，クランクシャフト１０８に，第２ローラ１１９を挿入する。
ステップ１０では，第２シリンダ１１５に，第２ベーン１１８を挿入する。
ステップ１１では，第２ベーン１１８をセットした第２シリンダ１１５と第２枠体１１６に設けられた第２軸受１１６ａをクランクシャフト１０８に挿入し，第２シリンダ１１５を仕切板１１４上に設置する。
ステップ１２では，第１軸受１０９ａと第２軸受１１６ａの中心が同軸となるように第２シリンダの位置決めを行う。
ステップ１３では，ボルトにより第１枠体１０９，第１シリンダ１１０，仕切板１１４，第２シリンダ１１５，第２枠体１１６を固定する。
In step 7, the first divided plate 130 and the second divided plate 131 are installed on the first cylinder 110. At this time, after measuring the plate thickness and selecting the first divided plate 130 from the stored divided plates, one second divided plate 131 is selected from a section thinner than the first divided plate 130, and these two sheets are selected. Are treated as a set of partition plates 114.
Then, the split surface 130c of the first split plate 130 and the second split plate 131 so that the intermediate portion 123 of the crankshaft 108 passes through the crankshaft insertion hole 132 formed by the first split plate 130 and the second split plate 131. The divided surfaces 131c are aligned.
In step 8, the partition plate 114 is positioned so that the inner periphery center of the partition plate 114 and the inner periphery center of the first cylinder 110 coincide.
In step 9, the second roller 119 is inserted into the crankshaft 108.
In step 10, the second vane 118 is inserted into the second cylinder 115.
In step 11, the second cylinder 115 on which the second vane 118 is set and the second bearing 116 a provided on the second frame 116 are inserted into the crankshaft 108, and the second cylinder 115 is installed on the partition plate 114.
In step 12, the second cylinder is positioned so that the centers of the first bearing 109a and the second bearing 116a are coaxial.
In step 13, the first frame 109, the first cylinder 110, the partition plate 114, the second cylinder 115, and the second frame 116 are fixed with bolts.
ここで第１分割板１３０と第２分割板１３１の板厚を測定後に保管する際に，上記では板厚5μmごとに区分して保管するとしたが，5μmという値に限ることではなく，適切な値ごとに区分してもよい。
また第１分割板１３０と第２分割板１３１の形状が等しい場合，板厚測定後に第１分割板１３０と第２分割板１３１をそれぞれ別々に保管する必要がなく，適当に選択した分割板を第１分割板１３０とし，第１分割板１３０よりわずかに薄い板厚の分割板を選択し第２分割板１３１とすることができ，保管する部品数を削減することができる。
Here, when the thickness of the first divided plate 130 and the second divided plate 131 is stored after measurement, the above is divided and stored for each thickness of 5 μm. However, the thickness is not limited to 5 μm, but is appropriate. You may classify by value.
In addition, when the shapes of the first divided plate 130 and the second divided plate 131 are the same, it is not necessary to store the first divided plate 130 and the second divided plate 131 separately after measuring the plate thickness. As the first divided plate 130, a divided plate slightly thinner than the first divided plate 130 can be selected and used as the second divided plate 131, and the number of parts to be stored can be reduced.
以上のような製造方法をとることで，加工のばらつきにより第１分割板１３０と第２分割板１３１の板厚に差が生じたとしても，微小隙間からの冷媒漏れによる性能低下のない多シリンダロータリ圧縮機を実現することができる。 By adopting the manufacturing method as described above, even if a difference occurs in the thickness of the first divided plate 130 and the second divided plate 131 due to processing variations, the multi-cylinder does not deteriorate in performance due to refrigerant leakage from a minute gap. A rotary compressor can be realized.
１００ 多シリンダロータリ圧縮機，１０１ シェル，１０２ モータ，１０３ 圧縮機構部，１０４ ガラス端子，１０５ 吐出パイプ，１０６ 吸入パイプ，１０７ 吸入マフラ，１０８ クランクシャフト，１０９ 第１枠体，１０９ａ 第１軸受，１１０ 第１シリンダ，１１１ 第１バネ，１１２ 第１ベーン，１１３ 第１ローラ，１１４ 仕切板，１１５ 第２シリンダ，１１６ 第２枠体，１１６ａ 第２軸受，１１７ 第２バネ，１１８ 第２ベーン，１１９ 第２ローラ，１２０ ロータ嵌合部，１２１ 第１軸受挿入部，１２２ 第１偏心部，１２３ 中間部，１２４ 第２偏心部，１２５ 第２軸受挿入部，１２６ 第1圧縮室，１２７ 第２圧縮室，１２８ 低圧部，１２９ 高圧部，１３０ 第１分割板，１３１ 第２分割板 100 multi-cylinder rotary compressor, 101 shell, 102 motor, 103 compression mechanism, 104 glass terminal, 105 discharge pipe, 106 suction pipe, 107 suction muffler, 108 crankshaft, 109 first frame, 109a first bearing, 110 1st cylinder, 111 1st spring, 112 1st vane, 113 1st roller, 114 Partition plate, 115 2nd cylinder, 116 2nd frame, 116a 2nd bearing, 117 2nd spring, 118 2nd vane, 119 Second roller, 120 Rotor fitting portion, 121 First bearing insertion portion, 122 First eccentric portion, 123 Intermediate portion, 124 Second eccentric portion, 125 Second bearing insertion portion, 126 First compression chamber, 127 Second compression Chamber, 128 low pressure section, 129 high pressure section, 130 first divided plate, 131 second divided plate
Claims (4)
上記圧縮機構部は，
軸方向に離間して配置された複数個の偏心部と，これらの偏心部の間に位置する中間部とを有し，上記モータにより駆動されるクランクシャフト，
上記複数個の偏心部外周に対応して配置された複数個のシリンダ，
上記クランクシャフトの軸受を有し，上記シリンダを挟むように上記クランクシャフトの軸方向両端部に設置された枠体，
上記クランクシャフトの中間部に挿入され，上記複数個のシリンダ間を仕切る仕切板，
及び上記クランクシャフトの偏心部外周に回転自在に取り付けられたローラ
を備え，
上記ローラ，上記シリンダ，上記枠体，及び上記仕切板で囲まれる空間を圧縮室として形成すると共に，上記ローラと摺動するように上記シリンダに保持されたベーンにより，上記圧縮室を低圧部と高圧部に分ける多シリンダロータリ圧縮機において，
上記仕切板はその径方向の中心線に沿って分割された２つの分割板で構成され，上記ベーンに接する側の分割板の板厚が他方の分割板の板厚より大きく設定されたことを特徴とする多シリンダロータリ圧縮機。 A motor and a compression mechanism are provided in the sealed container.
The compression mechanism is
A crankshaft having a plurality of eccentric parts spaced apart in the axial direction and an intermediate part located between the eccentric parts and driven by the motor;
A plurality of cylinders arranged corresponding to the outer circumferences of the plurality of eccentric parts;
A frame having bearings for the crankshaft and installed at both axial ends of the crankshaft so as to sandwich the cylinder;
A partition plate inserted between the crankshafts and separating the plurality of cylinders;
And a roller rotatably attached to the outer periphery of the eccentric portion of the crankshaft,
A space surrounded by the roller, the cylinder, the frame, and the partition plate is formed as a compression chamber, and the compression chamber is separated from the low pressure portion by a vane that is held in the cylinder so as to slide with the roller. In a multi-cylinder rotary compressor divided into high pressure parts,
The partition plate is composed of two split plates divided along the radial center line, and the thickness of the split plate on the side in contact with the vane is set larger than the thickness of the other split plate. A featured multi-cylinder rotary compressor.
上記ローラ，上記シリンダ，上記枠体，及び上記仕切板で囲まれる空間を圧縮室として形成すると共に，上記ローラと摺動するように上記シリンダに保持されたベーンにより，上記圧縮室を低圧部と高圧部に分けると共に，上記仕切板はその径方向の中心線に沿って分割された２つの分割板で構成され，上記ベーンに接する側の分割板の板厚が他方の分割板の板厚より大きく設定された多シリンダロータリ圧縮機の製造方法において，
上記分割板の板厚をそれぞれ測定して保管する工程と，
上記保管された分割板を組立に用いる場合，上記ベーンに接する側の分割板の板厚が他方の分割板の板厚より大きくなるように選択する工程と，
上記選択された分割板を上記シリンダ，及び上記枠体と締結する工程とを
含むことを特徴とする多シリンダロータリ圧縮機の製造方法。 A sealed container is provided with a motor and a compression mechanism, and the compression mechanism has a plurality of eccentric parts spaced apart in the axial direction, and an intermediate part located between the eccentric parts. A crankshaft driven by the motor, a plurality of cylinders arranged corresponding to the outer circumferences of the plurality of eccentric portions, bearings of the crankshaft, and both axial ends of the crankshaft so as to sandwich the cylinder A frame body installed at a portion, a partition plate that is inserted into an intermediate portion of the crankshaft and partitions the plurality of cylinders, and a roller that is rotatably attached to the outer periphery of the eccentric portion of the crankshaft,
A space surrounded by the roller, the cylinder, the frame, and the partition plate is formed as a compression chamber, and the compression chamber is separated from the low pressure portion by a vane that is held in the cylinder so as to slide with the roller. The partition plate is composed of two divided plates divided along the radial center line, and the thickness of the divided plate on the side in contact with the vane is greater than the thickness of the other divided plate. In the manufacturing method of a large-cylinder multi-cylinder rotary compressor,
Measuring and storing the thickness of each of the divided plates;
When the stored divided plate is used for assembly, the step of selecting the thickness of the divided plate on the side in contact with the vane to be larger than the thickness of the other divided plate;
A method for manufacturing a multi-cylinder rotary compressor, comprising the step of fastening the selected divided plate to the cylinder and the frame.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009264973A JP4897867B2 (en) | 2009-11-20 | 2009-11-20 | Multi-cylinder rotary compressor and manufacturing method thereof |
| CN 201010171680 CN102072156B (en) | 2009-11-20 | 2010-04-28 | Multi-cylinder rotary compressor and manufacture method thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009264973A JP4897867B2 (en) | 2009-11-20 | 2009-11-20 | Multi-cylinder rotary compressor and manufacturing method thereof |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2011106427A JP2011106427A (en) | 2011-06-02 |
| JP4897867B2 true JP4897867B2 (en) | 2012-03-14 |
Family
ID=44030847
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2009264973A Expired - Fee Related JP4897867B2 (en) | 2009-11-20 | 2009-11-20 | Multi-cylinder rotary compressor and manufacturing method thereof |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4897867B2 (en) |
| CN (1) | CN102072156B (en) |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5683384B2 (en) * | 2011-06-02 | 2015-03-11 | 三菱電機株式会社 | Multi-cylinder rotary compressor |
| JP2013007296A (en) * | 2011-06-23 | 2013-01-10 | Mitsubishi Electric Corp | Multi-cylinder rotary compressor and method of manufacturing the same |
| JP5683393B2 (en) * | 2011-06-24 | 2015-03-11 | 三菱電機株式会社 | Multi-cylinder rotary compressor |
| CZ306336B6 (en) * | 2011-10-25 | 2016-12-07 | Mitsubishi Electric Corporation | Multicylinder rotary compressor and method of attaching partition board between compression chambers thereof |
| JP5606422B2 (en) * | 2011-10-31 | 2014-10-15 | 三菱電機株式会社 | Rotary compressor |
| JP5781019B2 (en) * | 2012-06-13 | 2015-09-16 | 三菱電機株式会社 | Rotary compressor |
| JP6025500B2 (en) * | 2012-10-24 | 2016-11-16 | 三菱重工業株式会社 | Rotary compressor |
| JP6099550B2 (en) * | 2013-12-09 | 2017-03-22 | 三菱電機株式会社 | Vane type two-stage compressor |
| CN104389788A (en) * | 2014-09-22 | 2015-03-04 | 广东美芝制冷设备有限公司 | Compression mechanism for multi-cylinder rotary compressor and multi-cylinder rotary compressor |
| CN108825499A (en) * | 2018-08-03 | 2018-11-16 | 天津商业大学 | Three cylinder twin-stage compressor with rolling rotor of radial equipartition sliding slot |
| CN112229101B (en) * | 2020-10-26 | 2022-08-02 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor and air conditioning system |
| CN117189605B (en) * | 2023-11-06 | 2024-01-23 | 珠海格力电器股份有限公司 | Pump body structure and compressor using same |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59105993A (en) * | 1982-12-09 | 1984-06-19 | Mitsubishi Electric Corp | Multiple cylinder type rotary compressor |
| JPS63105786A (en) * | 1986-10-21 | 1988-05-11 | 三菱電機株式会社 | Automatic sewing machine |
| JPS63105786U (en) * | 1986-12-27 | 1988-07-08 | ||
| JPH109168A (en) * | 1996-06-28 | 1998-01-13 | Hitachi Ltd | Rotary compressor |
| JP2003328972A (en) * | 2002-05-09 | 2003-11-19 | Hitachi Home & Life Solutions Inc | Sealed two-cylinder rotary compressor and manufacturing method thereof |
-
2009
- 2009-11-20 JP JP2009264973A patent/JP4897867B2/en not_active Expired - Fee Related
-
2010
- 2010-04-28 CN CN 201010171680 patent/CN102072156B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN102072156A (en) | 2011-05-25 |
| JP2011106427A (en) | 2011-06-02 |
| CN102072156B (en) | 2013-06-12 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP4897867B2 (en) | Multi-cylinder rotary compressor and manufacturing method thereof | |
| KR101375979B1 (en) | Rotary compressor | |
| JP5284210B2 (en) | Rotary compressor, manufacturing method thereof, and manufacturing apparatus thereof | |
| JP5781019B2 (en) | Rotary compressor | |
| JP5084692B2 (en) | 2-cylinder rotary compressor | |
| US20210006103A1 (en) | Motor and compressor including the same | |
| US9145890B2 (en) | Rotary compressor with dual eccentric portion | |
| KR100432115B1 (en) | Plural cylinder rotary compressor | |
| KR101523435B1 (en) | Rotary compressor | |
| JP5679384B2 (en) | Multi-cylinder rotary compressor | |
| US8147220B2 (en) | Compressor having compression element welded to closed container at three or more welding points and suction tube neither parallel nor perpendicular to a straight line connecting any two of the welding points | |
| JP5606422B2 (en) | Rotary compressor | |
| JP5738423B2 (en) | Multi-cylinder rotary compressor and method for joining partition plates of compression chamber | |
| JP5766166B2 (en) | Rotary compressor | |
| KR101369053B1 (en) | Rotary compressor | |
| JP2015209778A (en) | Rotary compressor | |
| JP5766165B2 (en) | Rotary compressor | |
| JP6071787B2 (en) | Rotary compressor | |
| JP5734071B2 (en) | Rotary compressor and method for manufacturing the same | |
| JP2019011749A (en) | Rotary compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A621 | Written request for application examination |
Free format text: JAPANESE INTERMEDIATE CODE: A621 Effective date: 20111025 |
|
| TRDD | Decision of grant or rejection written | ||
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20111129 |
|
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 |
|
| A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20111222 |
|
| R151 | Written notification of patent or utility model registration |
Ref document number: 4897867 Country of ref document: JP Free format text: JAPANESE INTERMEDIATE CODE: R151 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20150106 Year of fee payment: 3 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| LAPS | Cancellation because of no payment of annual fees |