JP2019060307A

JP2019060307A - Rotary compressor

Info

Publication number: JP2019060307A
Application number: JP2017186703A
Authority: JP
Inventors: 泰幸泉; Yasuyuki Izumi
Original assignee: Fujitsu General Ltd
Current assignee: Fujitsu General Ltd
Priority date: 2017-09-27
Filing date: 2017-09-27
Publication date: 2019-04-18
Anticipated expiration: 2037-09-27
Also published as: JP6930338B2

Abstract

To inhibit lubrication oil in a rotary compressor from flowing out to the outside of the rotary compressor.SOLUTION: In a rotary compressor, lubrication oil for lubricating a compression part is housed in a compressor housing. An oil supply groove which extends from the lower side as seen in an axial direction of a rotary shaft to an upper end surface of a bearing part, has an opening on the upper end surface, and supplies the lubrication oil to the bearing part is formed on an inner peripheral surface of the bearing part. The bearing part of an upper end plate is inserted into an upper end plate cover discharge hole of an upper end plate cover, and a protruding part which blocks a refrigerant passing through a gap between the bearing part and the upper end plate cover discharge hole is formed at a position facing a range overlapping with the opening in a circumferential direction of the upper end plate cover discharge hole.SELECTED DRAWING: Figure 4

Description

本発明は、ロータリ圧縮機に関する。 The present invention relates to a rotary compressor.

例えば空気調和機や冷凍装置では、冷媒を圧縮するためにロータリ圧縮機が用いられている。ロータリ圧縮機は、圧縮機筐体内に配置された圧縮部の回転軸が軸受部に支持されており、軸受部が、圧縮部のシリンダの上側を閉塞する上端板に設けられている。この種のロータリ圧縮機では、軸受部等の摺動部分を適正に潤滑することで、例えば軸受部と回転軸との片当たりによる焼き付きを防ぐために、軸受部へ冷凍機油（以下、潤滑油と称する。）を供給する給油機構を有する。 For example, in an air conditioner or a refrigeration system, a rotary compressor is used to compress a refrigerant. In the rotary compressor, the rotary shaft of the compression unit disposed in the compressor housing is supported by the bearing unit, and the bearing unit is provided on the upper end plate closing the upper side of the cylinder of the compression unit. In this type of rotary compressor, by lubricating the sliding parts such as the bearing properly, for example, in order to prevent the seizing due to the contact between the bearing and the rotary shaft, the refrigeration machine oil (hereinafter referred to as lubricating oil) Supply mechanism) to supply the

また、軸受部が設けられた上端板は、上端板との間に上端板カバー室を形成する上端板カバーによって覆われている。上端板が有する吐出孔から吐出された冷媒は、上端板カバー室内を通り、上端板カバーの上端板カバー吐出孔から、圧縮機筐体内へ吐出される。上端板カバー吐出孔には、上端板の軸受部が通されており、上端板カバー吐出孔の内周面と軸受部の外周面との間の隙間から、上端板カバー室を通った冷媒が吐出される。 Further, the upper end plate provided with the bearing portion is covered by an upper end plate cover that forms an upper end plate cover chamber with the upper end plate. The refrigerant discharged from the discharge hole of the upper end plate passes through the upper end plate cover chamber, and is discharged into the compressor housing from the upper end plate cover discharge hole of the upper end plate cover. The bearing portion of the upper end plate is passed through the upper end plate cover discharge hole, and the refrigerant passing through the upper end plate cover chamber is from the gap between the inner peripheral surface of the upper end plate cover discharge hole and the outer peripheral surface of the bearing portion. It is discharged.

特開２０１５−４０４７２号公報JP, 2015-40472, A

上述したロータリ圧縮機の給油機構としては、圧縮機筐体内に収容された潤滑油を軸受部等へ供給する給油溝が軸受部の内周面に設けられており、給油溝が、回転軸の軸方向における下方から、軸受部の上端まで延ばされているものがある。この給油溝により、軸受部の上端まで送られた潤滑油が、この上端から軸受部の内周面の周方向へ広がると共に、内周面に沿って下方へ流れ落ちることにより、軸受部の内周面と回転軸の外周面との摺動部分全体へ潤滑油が供給される。 As an oil supply mechanism of the above-described rotary compressor, an oil supply groove for supplying lubricating oil contained in the compressor casing to the bearing portion and the like is provided on the inner peripheral surface of the bearing portion. There is one extending from the lower side in the axial direction to the upper end of the bearing portion. The lubricating oil fed to the upper end of the bearing portion spreads in the circumferential direction of the inner peripheral surface of the bearing portion from the upper end by this oil supply groove, and flows downward along the inner peripheral surface, whereby the inner periphery of the bearing portion The lubricating oil is supplied to the entire sliding portion between the surface and the outer peripheral surface of the rotating shaft.

このとき、軸受部の上端まで送られた潤滑油の一部が、軸受部の上端面に開口した給油溝の開口を経て軸受部の上端面を伝わり、軸受部の外周側へ溢れ出る場合がある。このように軸受部の外周側へ溢れ出た潤滑油は、軸受部の外周面と上端板カバーのカバー吐出孔の内周面との間の隙間から吐出される冷媒によって飛散され、冷媒と共にロータリ圧縮機の外部の冷媒循環回路へ流出してしまうおそれがある。 At this time, a part of the lubricating oil sent to the upper end of the bearing portion may pass through the opening of the oil supply groove opened at the upper end surface of the bearing portion, travel along the upper end surface of the bearing portion, and overflow to the outer peripheral side of the bearing portion is there. The lubricating oil that has spilled out to the outer peripheral side of the bearing portion in this way is scattered by the refrigerant discharged from the gap between the outer peripheral surface of the bearing portion and the inner peripheral surface of the cover discharge hole of the upper end plate cover. It may flow out to the refrigerant circulation circuit outside the compressor.

その結果、ロータリ圧縮機の内部に収容された潤滑油の量が少なくなり、軸受部等の摺動部分を適正に潤滑することが困難になる問題がある。また、ロータリ圧縮機の外部へ流出した潤滑油が、例えば、空気調和装置や冷凍装置の熱交換器の内部に付着することにより、熱交換性能の低下を招く問題がある。 As a result, the amount of lubricating oil contained inside the rotary compressor decreases, which makes it difficult to properly lubricate sliding parts such as bearings. In addition, the lubricating oil that has flowed out of the rotary compressor adheres, for example, to the inside of the heat exchanger of the air conditioner or the refrigeration apparatus, which causes a problem of lowering the heat exchange performance.

開示の技術は、上記に鑑みてなされたものであって、ロータリ圧縮機内の潤滑油がロータリ圧縮機の外部へ流出することを抑えることができるロータリ圧縮機を提供することを目的とする。 The technology disclosed herein has been made in view of the above, and it is an object of the present invention to provide a rotary compressor capable of suppressing the outflow of lubricating oil in the rotary compressor to the outside of the rotary compressor.

本願の開示するロータリ圧縮機の一態様は、上部に冷媒の吐出部が設けられ下部に冷媒の吸入部が設けられ密閉された縦置き円筒状の圧縮機筐体と、前記圧縮機筐体の下部に配置され前記吸入部から吸入された冷媒を圧縮し前記吐出部から吐出する圧縮部と、前記圧縮機筐体の上部に配置され前記圧縮部を駆動するモータと、を有し、前記圧縮部は、圧縮室を形成する環状のシリンダと、前記シリンダの上側を閉塞する上端板と、前記上端板に設けられた軸受部に支持され前記モータにより回転される回転軸と、前記上端板を覆って前記上端板との間に上端板カバー室を形成する上端板カバーと、前記上端板カバーに設けられ前記上端板カバー室と前記圧縮機筐体の内部とを連通する上端板カバー吐出孔と、前記上端板に設けられ前記圧縮室と前記上端板カバー室とを連通させる吐出孔と、を有するロータリ圧縮機において、前記圧縮機筐体には、前記圧縮部を潤滑する潤滑油が収容され、前記軸受部の内周面には、前記回転軸の軸方向における下方から前記軸受部の上端面まで延びて前記上端面に開口を有し前記潤滑油を前記軸受部に供給する給油溝が形成され、前記上端板カバーの前記上端板カバー吐出孔には、前記軸受部が通され、前記上端板カバー吐出孔の周方向において前記開口に重なる範囲に、前記軸受部と前記上端板カバー吐出孔との間の隙間を通過する冷媒を遮る凸部が形成されている。 One aspect of a rotary compressor disclosed in the present application includes a vertically disposed cylindrical compressor casing provided with a discharge unit for the refrigerant at the upper part and a suction unit for the refrigerant at the lower part and sealed, and the compressor case The compressor includes: a compression unit disposed in a lower part, compressing a refrigerant sucked from the suction part and discharging the refrigerant from the discharge part, and a motor disposed in an upper part of the compressor casing to drive the compression part The portion includes an annular cylinder forming a compression chamber, an upper end plate closing the upper side of the cylinder, a rotation shaft supported by a bearing portion provided on the upper end plate and rotated by the motor, and the upper end plate An upper end plate cover which covers and forms an upper end plate cover chamber between the upper end plate, and an upper end plate cover discharge hole which is provided on the upper end plate cover and which communicates the upper end plate cover chamber and the inside of the compressor housing And the compression chamber provided on the upper end plate In the rotary compressor having a discharge hole communicating with the upper end plate cover chamber, lubricating oil for lubricating the compression portion is accommodated in the compressor housing, and an inner peripheral surface of the bearing portion is provided with: An oil supply groove is formed extending from below in the axial direction of the rotary shaft to the upper end surface of the bearing portion and having an opening at the upper end surface to supply the lubricating oil to the bearing portion; the upper end plate of the upper end plate cover The cover discharge hole is passed through the bearing portion, and in a range overlapping the opening in the circumferential direction of the upper end plate cover discharge hole, the refrigerant passing through the clearance between the bearing portion and the upper end plate cover discharge hole A protruding convex portion is formed.

本願の開示するロータリ圧縮機の一態様によれば、ロータリ圧縮機内の潤滑油がロータリ圧縮機の外部へ流出することを抑えることができる。 According to one aspect of the rotary compressor disclosed in the present application, it is possible to prevent the lubricating oil in the rotary compressor from flowing out of the rotary compressor.

図１は、実施例のロータリ圧縮機を示す縦断面図である。FIG. 1 is a longitudinal sectional view showing a rotary compressor of the embodiment. 図２は、実施例のロータリ圧縮機の圧縮部を示す分解斜視図である。FIG. 2 is an exploded perspective view showing the compression unit of the rotary compressor of the embodiment. 図３は、実施例のロータリ圧縮機の上端板カバーの上端板カバー吐出孔が有する凸部を示す斜視図である。FIG. 3 is a perspective view showing a convex portion of the upper end plate cover discharge hole of the upper end plate cover of the rotary compressor of the embodiment. 図４は、実施例のロータリ圧縮機の上端板カバーの上端板カバー吐出孔と主軸受部との間の隙間を上方から見た平面図である。FIG. 4 is a plan view of the gap between the upper end plate cover discharge hole of the upper end plate cover of the rotary compressor of the embodiment and the main bearing as viewed from above. 図５は、実施例のロータリ圧縮機の上端板の主軸受部との間の隙間を上方から見た平面図である。FIG. 5 is a plan view of the gap between the upper bearing and the main bearing portion of the upper end plate of the rotary compressor of the embodiment as viewed from above. 図６は、実施例のロータリ圧縮機の上端板カバーを上方から見た平面図である。FIG. 6 is a plan view of the upper end plate cover of the rotary compressor of the embodiment as viewed from above. 図７は、他の実施例のロータリ圧縮機の上端板カバーの上端板カバー吐出孔と主軸受部との間の隙間を上方から見た平面図である。FIG. 7 is a plan view of the gap between the upper end plate cover discharge hole of the upper end plate cover of the rotary compressor of another embodiment and the main bearing as viewed from above. 図８は、他の実施例のロータリ圧縮機の上端板カバーを上方から見た平面図である。FIG. 8 is a plan view of the upper end plate cover of the rotary compressor of another embodiment as viewed from above. 図９は、他の実施例のロータリ圧縮機の変形例１としての、上端板カバー吐出孔と主軸受部との間の隙間を上方から見た拡大平面図である。FIG. 9 is an enlarged plan view of a gap between the upper end plate cover discharge hole and the main bearing portion as a first modification of the rotary compressor according to another embodiment as viewed from above. 図１０は、他の実施例のロータリ圧縮機の変形例２としての、上端板カバー吐出孔と主軸受部との間の隙間を上方から見た拡大平面図である。FIG. 10 is an enlarged plan view of the gap between the upper end plate cover discharge hole and the main bearing portion as a modification 2 of the rotary compressor of the other embodiment as viewed from above.

以下に、本願の開示するロータリ圧縮機の実施例を図面に基づいて説明する。なお、以下の実施例によって、本願の開示するロータリ圧縮機が限定されるものではない。 Hereinafter, an embodiment of a rotary compressor disclosed in the present application will be described based on the drawings. Note that the rotary compressor disclosed in the present application is not limited by the following embodiments.

（ロータリ圧縮機の構成）
図１は、実施例のロータリ圧縮機を示す縦断面図である。図２は、実施例のロータリ圧縮機の圧縮部を示す分解斜視図である。 (Configuration of rotary compressor)
FIG. 1 is a longitudinal sectional view showing a rotary compressor of the embodiment. FIG. 2 is an exploded perspective view showing the compression unit of the rotary compressor of the embodiment.

図１に示すように、ロータリ圧縮機１は、密閉された縦置き円筒状の圧縮機筐体１０内の下部に配置された圧縮部１２と、圧縮機筐体１０内の上部に配置され回転軸１５を介して圧縮部１２を駆動するモータ１１と、圧縮機筐体１０の外周面に固定され密閉された縦置き円筒状のアキュムレータ２５と、を備えている。 As shown in FIG. 1, the rotary compressor 1 is disposed at the upper portion in the compressor case 10 and the compression unit 12 disposed in the lower portion in the hermetically sealed vertically placed cylindrical compressor case 10, and is rotated. The motor 11 drives the compression unit 12 via the shaft 15, and a vertically placed cylindrical accumulator 25 fixed to the outer peripheral surface of the compressor housing 10 and sealed.

圧縮機筐体１０は、冷媒を吸入する上吸入管１０５及び下吸入管１０４を有しており、上吸入管１０５及び下吸入管１０４が圧縮機筐体１０の側面下部に設けられている。アキュムレータ２５は、吸入部としての上吸入管１０５及びアキュムレータ上湾曲管３１Ｔを介して上シリンダ１２１Ｔの上シリンダ室１３０Ｔ（図２参照）と接続され、吸入部としての下吸入管１０４及びアキュムレータ下湾曲管３１Ｓを介して下シリンダ１２１Ｓの下シリンダ室１３０Ｓ（図２参照）と接続されている。本実施例では、圧縮機筐体１０の周方向において、上吸入管１０５と下吸入管１０４の位置が重なっており、同一位置に位置する。 The compressor housing 10 has an upper suction pipe 105 and a lower suction pipe 104 for suctioning the refrigerant, and the upper suction pipe 105 and the lower suction pipe 104 are provided at the lower side of the side surface of the compressor housing 10. The accumulator 25 is connected to the upper cylinder chamber 130T (see FIG. 2) of the upper cylinder 121T via the upper suction pipe 105 as the suction portion and the accumulator upper curved pipe 31T, and the lower suction pipe 104 and the accumulator lower curvature as the suction portion The lower cylinder 121S is connected to the lower cylinder chamber 130S (see FIG. 2) through the pipe 31S. In the present embodiment, in the circumferential direction of the compressor housing 10, the positions of the upper suction pipe 105 and the lower suction pipe 104 overlap and are located at the same position.

モータ１１は、外側に配置されたステータ１１１と、内側に配置されたロータ１１２と、を備えている。ステータ１１１は、圧縮機筐体１０の内周面に焼嵌めまたは溶接によって固定されている。ロータ１１２は、回転軸１５に焼嵌めによって固定されている。 The motor 11 includes a stator 111 disposed outside and a rotor 112 disposed inside. The stator 111 is fixed to the inner peripheral surface of the compressor housing 10 by shrink fitting or welding. The rotor 112 is fixed to the rotating shaft 15 by shrink fitting.

回転軸１５は、下偏芯部１５２Ｓの下方の副軸部１５１が、下端板１６０Ｓに設けられた副軸受部１６１Ｓに回転自在に支持され、上偏芯部１５２Ｔの上方の主軸部１５３が上端板１６０Ｔに設けられた軸受部としての主軸受部１６１Ｔに回転自在に支持されている。回転軸１５には、上偏芯部１５２Ｔと下偏芯部１５２Ｓとが互いに１８０度の位相差をつけて設けられており、上偏芯部１５２Ｔに上ピストン１２５Ｔが支持され、下偏芯部１５２Ｓに下ピストン１２５Ｓが支持されている。これによって、回転軸１５は、圧縮部１２全体に対して回転自在に支持されると共に、回転によって上ピストン１２５Ｔの外周面１３９Ｔを上シリンダ１２１Ｔの内周面１３７Ｔに沿って公転運動させ、下ピストン１２５Ｓの外周面１３９Ｓを下シリンダ１２１Ｓの内周面１３７Ｓに沿って公転運動させる。 The lower shaft portion 151 of the lower eccentric portion 152S is rotatably supported by the auxiliary bearing portion 161S provided on the lower end plate 160S, and the main shaft portion 153 above the upper eccentric portion 152T is an upper end of the rotary shaft 15 It is rotatably supported by a main bearing portion 161T as a bearing portion provided on the plate 160T. An upper eccentricity portion 152T and a lower eccentricity portion 152S are provided on the rotation shaft 15 with a phase difference of 180 degrees to each other, and the upper piston 125T is supported by the upper eccentricity portion 152T, and the lower eccentricity portion The lower piston 125S is supported by 152S. Thus, the rotary shaft 15 is rotatably supported by the entire compression unit 12 and, by rotation, causes the outer circumferential surface 139T of the upper piston 125T to revolve along the inner circumferential surface 137T of the upper cylinder 121T. The outer peripheral surface 139S of 125S is revolved along the inner peripheral surface 137S of the lower cylinder 121S.

圧縮機筐体１０の内部には、圧縮部１２において摺動する上シリンダ１２１Ｔと上ピストン１２５Ｔ及び下シリンダ１２１Ｓと下ピストン１２５Ｓ等の摺動部分の潤滑性を確保し、上圧縮室１３３Ｔ（図２参照）及び下圧縮室１３３Ｓ（図２参照）をシールするための潤滑油（冷凍機油）１８が、圧縮部１２をほぼ浸漬する量だけ封入されている。圧縮機筐体１０の下側には、ロータリ圧縮機１全体を支持する複数の弾性支持部材（図示せず）を係止する取付脚３１０（図１参照）が固定されている。 Inside the compressor housing 10, the lubricity of the sliding parts such as the upper cylinder 121T, the upper piston 125T, the lower cylinder 121S and the lower piston 125S sliding in the compression section 12 is secured, and the upper compression chamber 133T (see FIG. 2) and lubricating oil (refrigerant oil) 18 for sealing the lower compression chamber 133S (see FIG. 2) are sealed so that the compression section 12 is substantially immersed. On the lower side of the compressor housing 10, a mounting leg 310 (see FIG. 1) for locking a plurality of elastic support members (not shown) for supporting the entire rotary compressor 1 is fixed.

図１に示すように、圧縮部１２は、上吸入管１０５及び下吸入管１０４から吸入された冷媒を圧縮し、後述する吐出管１０７から吐出する。図２に示すように、圧縮部１２は、上から、内部に中空空間が形成された膨出部１８１を有する上端板カバー１７０Ｔ、上端板１６０Ｔ、環状の上シリンダ１２１Ｔ、中間仕切板１４０、環状の下シリンダ１２１Ｓ、下端板１６０Ｓ及び平板状の下端板カバー１７０Ｓを積層して構成されている。圧縮部１２全体は、上下から略同心円上に配置された複数の通しボルト１７４，１７５及び補助ボルト１７６によって固定されている。 As shown in FIG. 1, the compression unit 12 compresses the refrigerant drawn from the upper suction pipe 105 and the lower suction pipe 104 and discharges the refrigerant from a discharge pipe 107 described later. As shown in FIG. 2, the compression unit 12 includes, from the top, an upper end plate cover 170T having an expanded portion 181 in which a hollow space is formed inside, an upper end plate 160T, an annular upper cylinder 121T, an intermediate partition plate 140, and an annular The lower cylinder 121S, the lower end plate 160S, and the flat lower end plate cover 170S are stacked. The entire compression section 12 is fixed by a plurality of through bolts 174 and 175 and an auxiliary bolt 176 which are disposed substantially concentrically from above and below.

上シリンダ１２１Ｔには、円筒状の内周面１３７Ｔが形成されている。上シリンダ１２１Ｔの内周面１３７Ｔの内側には、上シリンダ１２１Ｔの内周面１３７Ｔの内径よりも小さい外径の上ピストン１２５Ｔが配置されており、上シリンダ１２１Ｔの内周面１３７Ｔと上ピストン１２５Ｔの外周面１３９Ｔとの間に、冷媒を吸入し圧縮して吐出する上圧縮室１３３Ｔが形成される。下シリンダ１２１Ｓには、円筒状の内周面１３７Ｓが形成されている。下シリンダ１２１Ｓの内周面１３７Ｓの内側には、下シリンダ１２１Ｓの内周面１３７Ｓの内径よりも小さい外径の下ピストン１２５Ｓが配置されており、下シリンダ１２１Ｓの内周面１３７Ｓと下ピストン１２５Ｓの外周面１３９Ｓとの間に、冷媒を吸入し圧縮して吐出する下圧縮室１３３Ｓが形成される。 A cylindrical inner circumferential surface 137T is formed on the upper cylinder 121T. An upper piston 125T having an outer diameter smaller than the inner diameter of the inner peripheral surface 137T of the upper cylinder 121T is disposed inside the inner peripheral surface 137T of the upper cylinder 121T, and the inner peripheral surface 137T of the upper cylinder 121T and the upper piston 125T are disposed. An upper compression chamber 133T for suctioning, compressing and discharging the refrigerant is formed between the outer peripheral surface 139T and the outer peripheral surface 139T. A cylindrical inner circumferential surface 137S is formed on the lower cylinder 121S. The lower piston 125S having an outer diameter smaller than the inner diameter of the inner peripheral surface 137S of the lower cylinder 121S is disposed inside the inner peripheral surface 137S of the lower cylinder 121S, and the inner peripheral surface 137S of the lower cylinder 121S and the lower piston 125S A lower compression chamber 133S for suctioning, compressing and discharging the refrigerant is formed between the outer peripheral surface 139S and the lower peripheral surface 139S.

図２に示すように、上シリンダ１２１Ｔは、外周部から、円筒状の内周面１３７Ｔの径方向における外周側へ張り出した上側方突出部１２２Ｔを有する。上側方突出部１２２Ｔには、上シリンダ室１３０Ｔから放射状に外方へ延びる上ベーン溝１２８Ｔが設けられている。上ベーン溝１２８Ｔ内には、上ベーン１２７Ｔが摺動可能に配置されている。下シリンダ１２１Ｓは、外周部から、円筒状の内周面１３７Ｓの径方向における外周側へ張り出した下側方突出部１２２Ｓを有する。下側方突出部１２２Ｓには、下シリンダ室１３０Ｓから放射状に外方へ延びる下ベーン溝１２８Ｓが設けられている。下ベーン溝１２８Ｓ内には、下ベーン１２７Ｓが摺動可能に配置されている。 As shown in FIG. 2, the upper cylinder 121T has an upper side protruding portion 122T that protrudes from the outer peripheral portion to the outer peripheral side in the radial direction of the cylindrical inner peripheral surface 137T. An upper vane groove 128T extending radially outward from the upper cylinder chamber 130T is provided in the upper side protrusion 122T. An upper vane 127T is slidably disposed in the upper vane groove 128T. The lower cylinder 121S has a lower side projecting portion 122S protruding from the outer peripheral portion to the outer peripheral side in the radial direction of the cylindrical inner peripheral surface 137S. The lower protrusion 122S is provided with a lower vane groove 128S extending radially outward from the lower cylinder chamber 130S. A lower vane 127S is slidably disposed in the lower vane groove 128S.

上側方突出部１２２Ｔは、上シリンダ１２１Ｔの内周面１３７Ｔの周方向に沿って、所定の突出範囲にわたって形成されている。下側方突出部１２２Ｓは、下シリンダ１２１Ｓの内周面１３７Ｓの周方向に沿って、所定の突出範囲にわたって形成されている。上側方突出部１２２Ｔ及び下側方突出部１２２Ｓは、上シリンダ１２１Ｔ及び下シリンダ１２１Ｓの加工時に加工治具に固定するためのチャック用保持部として用いられる。上側方突出部１２２Ｔ及び下側方突出部１２２Ｓが加工治具に固定されることで、上シリンダ１２１Ｔ及び下シリンダ１２１Ｓが所定の位置に位置決めされる。 The upper side protruding portion 122T is formed over a predetermined protruding range along the circumferential direction of the inner peripheral surface 137T of the upper cylinder 121T. The lower protruding portion 122S is formed over a predetermined protruding range along the circumferential direction of the inner circumferential surface 137S of the lower cylinder 121S. The upper side protruding portion 122T and the lower side protruding portion 122S are used as a chuck holding portion for fixing to the processing jig when the upper cylinder 121T and the lower cylinder 121S are processed. By fixing the upper side protrusion 122T and the lower side protrusion 122S to the processing jig, the upper cylinder 121T and the lower cylinder 121S are positioned at predetermined positions.

上側方突出部１２２Ｔには、外側面から上ベーン溝１２８Ｔと重なる位置に、上シリンダ室１３０Ｔに貫通しない深さで上スプリング穴１２４Ｔが設けられている。上スプリング穴１２４Ｔには上スプリング１２６Ｔが配置されている。下側方突出部１２２Ｓには、外側面から下ベーン溝１２８Ｓと重なる位置に、下シリンダ室１３０Ｓに貫通しない深さで下スプリング穴１２４Ｓが設けられている。下スプリング穴１２４Ｓには下スプリング１２６Ｓが配置されている。 An upper spring hole 124T is provided in the upper side protruding portion 122T at a position not overlapping the upper cylinder chamber 130T at a position overlapping the upper vane groove 128T from the outer side surface. An upper spring 126T is disposed in the upper spring hole 124T. A lower spring hole 124S is provided in the lower protrusion 122S at a position overlapping the lower vane groove 128S from the outer side surface with a depth not penetrating the lower cylinder chamber 130S. A lower spring 126S is disposed in the lower spring hole 124S.

また、上シリンダ１２１Ｔには、上ベーン溝１２８Ｔの径方向外側と圧縮機筐体１０内とを開口部で連通して圧縮機筐体１０内の圧縮された冷媒を導入し、上ベーン１２７Ｔに冷媒の圧力により背圧をかける上圧力導入路が形成されている。また、下シリンダ１２１Ｓには、下ベーン溝１２８Ｓの径方向外側と圧縮機筐体１０内とを連通して圧縮機筐体１０内の圧縮された冷媒を導入し、下ベーン１２７Ｓに冷媒の圧力により背圧をかける下圧力導入路１２９Ｓが形成されている。 Further, the upper cylinder 121T communicates the radially outer side of the upper vane groove 128T with the inside of the compressor housing 10 at the opening to introduce the compressed refrigerant in the compressor housing 10, and the upper vane 127T is An upper pressure introduction path is formed to apply a back pressure by the pressure of the refrigerant. Further, the compressed refrigerant in the compressor housing 10 is introduced into the lower cylinder 121S by communicating the radially outer side of the lower vane groove 128S with the inside of the compressor housing 10, and the pressure of the refrigerant in the lower vane 127S Thus, a lower pressure introducing passage 129S for applying a back pressure is formed.

上シリンダ１２１Ｔの上側方突出部１２２Ｔには、上吸入管１０５と嵌合する上吸入孔１３５Ｔが設けられている。下シリンダ１２１Ｓの下側方突出部１２２Ｓには、下吸入管１０４と嵌合する下吸入孔１３５Ｓが設けられている。 An upper suction hole 135T that engages with the upper suction pipe 105 is provided in the upper side protruding portion 122T of the upper cylinder 121T. A lower suction hole 135S fitted with the lower suction pipe 104 is provided in the lower side projecting portion 122S of the lower cylinder 121S.

図２に示すように、上シリンダ室１３０Ｔは、上側が上端板１６０Ｔで閉塞され、下側が中間仕切板１４０で閉塞されている。下シリンダ室１３０Ｓは、上側が中間仕切板１４０で閉塞され、下側が下端板１６０Ｓで閉塞されている。 As shown in FIG. 2, the upper side of the upper cylinder chamber 130T is closed by the upper end plate 160T, and the lower side is closed by the intermediate partition plate 140. The upper side of the lower cylinder chamber 130S is closed by the intermediate partition plate 140, and the lower side is closed by the lower end plate 160S.

上シリンダ室１３０Ｔは、上ベーン１２７Ｔが上スプリング１２６Ｔに押圧されて上ピストン１２５Ｔの外周面１３９Ｔに当接することによって、上吸入孔１３５Ｔに連通する上吸入室１３１Ｔと、上端板１６０Ｔに設けられた上吐出孔１９０Ｔに連通する上圧縮室１３３Ｔと、に区画される。下シリンダ室１３０Ｓは、下ベーン１２７Ｓが下スプリング１２６Ｓに押圧されて下ピストン１２５Ｓの外周面１３９Ｓに当接することによって、下吸入孔１３５Ｓに連通する下吸入室１３１Ｓと、下端板１６０Ｓに設けられた下吐出孔１９０Ｓに連通する下圧縮室１３３Ｓと、に区画される。 The upper cylinder chamber 130T is provided in the upper suction chamber 131T communicated with the upper suction hole 135T and the upper end plate 160T when the upper vane 127T is pressed by the upper spring 126T and abuts on the outer peripheral surface 139T of the upper piston 125T. It is divided into an upper compression chamber 133T communicating with the upper discharge hole 190T. The lower cylinder chamber 130S is provided in the lower suction chamber 131S communicating with the lower suction hole 135S and the lower end plate 160S when the lower vane 127S is pressed by the lower spring 126S and abuts on the outer peripheral surface 139S of the lower piston 125S. It is divided into a lower compression chamber 133S communicating with the lower discharge hole 190S.

また、上吐出孔１９０Ｔは、上ベーン溝１２８Ｔに近接して設けられており、下吐出孔１９０Ｓは、下ベーン溝１２８Ｓに近接して設けられている。上圧縮室１３３Ｔ内で圧縮された冷媒は、上圧縮室１３３Ｔ内から上吐出孔１９０Ｔを通って吐出される。下圧縮室１３３Ｓ内で圧縮された冷媒は、下圧縮室１３３Ｓ内から下吐出孔１９０Ｓを通って吐出される。 Further, the upper discharge hole 190T is provided in proximity to the upper vane groove 128T, and the lower discharge hole 190S is provided in proximity to the lower vane groove 128S. The refrigerant compressed in the upper compression chamber 133T is discharged from the upper compression chamber 133T through the upper discharge hole 190T. The refrigerant compressed in the lower compression chamber 133S is discharged from the lower compression chamber 133S through the lower discharge hole 190S.

図２に示すように、上端板１６０Ｔには、上端板１６０Ｔを貫通して上シリンダ１２１Ｔの上圧縮室１３３Ｔと連通する上吐出孔１９０Ｔが設けられている。上吐出孔１９０Ｔの出口側には、上吐出孔１９０Ｔの周囲に上弁座が形成されている。上端板１６０Ｔの上側（上端板カバー１７０Ｔ側）には、上吐出孔１９０Ｔの位置から上端板１６０Ｔの外周に向かって溝状に延びる上吐出弁収容凹部１６４Ｔが形成されている。 As shown in FIG. 2, the upper end plate 160T is provided with an upper discharge hole 190T which penetrates the upper end plate 160T and communicates with the upper compression chamber 133T of the upper cylinder 121T. An upper valve seat is formed around the upper discharge hole 190T on the outlet side of the upper discharge hole 190T. On the upper side (upper end plate cover 170T side) of the upper end plate 160T, an upper discharge valve accommodation concave portion 164T extending in a groove shape from the position of the upper discharge hole 190T toward the outer periphery of the upper end plate 160T is formed.

上吐出弁収容凹部１６４Ｔ内には、リード弁型の上吐出弁２００Ｔ全体と、上吐出弁２００Ｔの開度を規制する上吐出弁押さえ２０１Ｔ全体とが収容されている。上吐出弁２００Ｔは、基端部が上吐出弁収容凹部１６４Ｔ内に上リベット２０２Ｔにより固定されており、先端部が上吐出孔１９０Ｔを開閉する。上吐出弁押さえ２０１Ｔは、基端部が上吐出弁２００Ｔに重ねられて上吐出弁収容凹部１６４Ｔ内に上リベット２０２Ｔにより固定されており、先端部が上吐出弁２００Ｔが開く方向へ湾曲して（反って）いて上吐出弁２００Ｔの開度を規制する。また、上吐出弁収容凹部１６４Ｔは、その幅が上吐出弁２００Ｔ及び上吐出弁押さえ２０１Ｔの幅よりわずかに大きく形成されており、上吐出弁２００Ｔ及び上吐出弁押さえ２０１Ｔを収容すると共に、上吐出弁２００Ｔ及び上吐出弁押さえ２０１Ｔを位置決めしている。 In the upper discharge valve accommodation recess 164T, the entire reed valve type upper discharge valve 200T and the entire upper discharge valve press 201T that regulates the opening degree of the upper discharge valve 200T are accommodated. The upper discharge valve 200T is fixed at its base end portion in the upper discharge valve accommodating recess 164T by the upper rivet 202T, and its tip end opens and closes the upper discharge hole 190T. The upper discharge valve holder 201T has its base end superimposed on the upper discharge valve 200T and is fixed in the upper discharge valve accommodation recess 164T by the upper rivet 202T, and its tip is curved in the direction in which the upper discharge valve 200T opens. Then, the opening degree of the upper discharge valve 200T is restricted. The upper discharge valve accommodating recess 164T has a width slightly larger than the widths of the upper discharge valve 200T and the upper discharge valve retainer 201T, and accommodates the upper discharge valve 200T and the upper discharge valve retainer 201T. The discharge valve 200T and the upper discharge valve retainer 201T are positioned.

図２に示すように、下端板１６０Ｓには、下端板１６０Ｓを貫通して下シリンダ１２１Ｓの下圧縮室１３３Ｓと連通する下吐出孔１９０Ｓが設けられている。下吐出孔１９０Ｓの出口側には、下吐出孔１９０Ｓの周囲に環状の下弁座が形成されている。下端板１６０Ｓの下側（下端板カバー１７０Ｓ側）には、下吐出孔１９０Ｓの位置から下端板１６０Ｓの外周に向かって溝状に延びる下吐出弁収容凹部（不図示）が形成されている。 As shown in FIG. 2, the lower end plate 160S is provided with a lower discharge hole 190S which penetrates the lower end plate 160S and communicates with the lower compression chamber 133S of the lower cylinder 121S. An annular lower valve seat is formed around the lower discharge hole 190S on the outlet side of the lower discharge hole 190S. A lower discharge valve housing recess (not shown) extending in a groove shape from the position of the lower discharge hole 190S toward the outer periphery of the lower end plate 160S is formed on the lower side (lower end plate cover 170S side) of the lower end plate 160S.

下吐出弁収容凹部１６４Ｓ内には、リード弁型の下吐出弁２００Ｓ全体と、下吐出弁２００Ｓの開度を規制する下吐出弁押さえ２０１Ｓ全体とが収容されている。下吐出弁２００Ｓは、基端部が下吐出弁収容凹部１６４Ｓ内に下リベット２０２Ｓにより固定されており、先端部が下吐出孔１９０Ｓを開閉する。下吐出弁押さえ２０１Ｓは、基端部が下吐出弁２００Ｓに重ねられて下吐出弁収容凹部１６４Ｓ内に下リベット２０２Ｓにより固定されており、先端部が下吐出弁２００Ｓが開く方向へ湾曲して（反って）いて下吐出弁２００Ｓの開度を規制する。また、下吐出弁収容凹部１６４Ｓは、その幅が下吐出弁２００Ｓ及び下吐出弁押さえ２０１Ｓの幅よりわずかに大きく形成されており、下吐出弁２００Ｓ及び下吐出弁押さえ２０１Ｓを収容すると共に、下吐出弁２００Ｓ及び下吐出弁押さえ２０１Ｓを位置決めしている。 In the lower discharge valve housing recess 164S, the entire reed valve type lower discharge valve 200S and the entire lower discharge valve press 201S for regulating the opening degree of the lower discharge valve 200S are stored. The lower discharge valve 200S has a base end fixed to the lower discharge valve receiving recess 164S by the lower rivet 202S, and a distal end opens and closes the lower discharge hole 190S. The lower discharge valve presser 201S has a base end superimposed on the lower discharge valve 200S and is fixed in the lower discharge valve receiving recess 164S by the lower rivet 202S, and the tip is curved in the direction in which the lower discharge valve 200S opens. Then, the opening degree of the lower discharge valve 200S is regulated. The lower discharge valve accommodating recess 164S is formed to have a width slightly larger than the widths of the lower discharge valve 200S and the lower discharge valve retainer 201S, and accommodates the lower discharge valve 200S and the lower discharge valve retainer 201S. The discharge valve 200S and the lower discharge valve press 201S are positioned.

また、互いに密着固定された上端板１６０Ｔと、膨出部１８１を有する上端板カバー１７０Ｔとの間には、上端板カバー室１８０Ｔが形成される。互いに密着固定された下端板１６０Ｓと平板状の下端板カバー１７０Ｓとの間には、下端板カバー室１８０Ｓが形成される。下端板１６０Ｓ、下シリンダ１２１Ｓ、中間仕切板１４０、上端板１６０Ｔ及び上シリンダ１２１Ｔを貫通し下端板カバー室１８０Ｓと上端板カバー室１８０Ｔとを連通する複数の冷媒通路孔１３６が設けられている。 Further, an upper end plate cover chamber 180T is formed between the upper end plate 160T tightly fixed to each other and the upper end plate cover 170T having the bulging portion 181. A lower end plate cover chamber 180S is formed between the lower end plate 160S closely attached and fixed to each other and the flat lower end plate cover 170S. A plurality of refrigerant passage holes 136 which penetrate the lower end plate 160S, the lower cylinder 121S, the middle partition plate 140, the upper end plate 160T and the upper cylinder 121T and connect the lower end plate cover chamber 180S and the upper end plate cover chamber 180T are provided.

上端板１６０Ｔに形成された上吐出室凹部１６３Ｔ及び上吐出弁収容凹部１６４Ｔについては、詳細な図示を省略するが、下端板１６０Ｓに形成された下吐出室凹部１６３Ｓ及び下吐出弁収容凹部１６４Ｓと同様の形状に形成されている。上端板カバー室１８０Ｔは、上端板カバー１７０Ｔのドーム状の膨出部１８１と上吐出室凹部１６３Ｔと上吐出弁収容凹部１６４Ｔとによって形成されている。 The upper discharge chamber concave portion 163T and the upper discharge valve housing concave portion 164T formed in the upper end plate 160T are not shown in detail but a lower discharge chamber concave portion 163S and a lower discharge valve housing concave portion 164S formed in the lower end plate 160S It is formed in the same shape. The upper end plate cover chamber 180T is formed of a dome-like bulging portion 181 of the upper end plate cover 170T, an upper discharge chamber concave portion 163T, and an upper discharge valve accommodation concave portion 164T.

図２に示すように、上端板カバー１７０Ｔの外縁部には、略同心円上に複数のボルト孔１７３Ｔが設けられており、上端板カバー１７０Ｔ側からボルト孔１７３Ｔに挿入された通しボルト１７４（図２）によって上端板１６０Ｔに固定されている。上端板カバー１７０Ｔの膨出部１８１は、回転軸１５の径方向において、回転軸１５側から、隣り合う通しボルト１７４の間に向かって張出す複数の張出し部１８２と、各張出し部１８２の間をつなぐと共に通しボルト１７４（ボルト孔１７３Ｔ）よりも回転軸１５側へ窪んで形成された複数の窪み部１８３と、を有する。 As shown in FIG. 2, a plurality of bolt holes 173T are provided substantially concentrically at the outer edge portion of the upper end plate cover 170T, and a through bolt 174 inserted into the bolt hole 173T from the upper end plate cover 170T side (see FIG. It is being fixed to the upper end plate 160T by 2). The bulging portion 181 of the upper end plate cover 170T is between the respective bulging portions 182 and a plurality of bulging portions 182 which are bulging toward the space between the adjacent through bolts 174 from the rotary shaft 15 side in the radial direction of the rotary shaft 15. And a plurality of depressions 183 formed on the rotation shaft 15 side with respect to the through bolt 174 (bolt hole 173T).

以下に、回転軸１５の回転による冷媒の流れを説明する。上シリンダ室１３０Ｔ内において、回転軸１５の回転によって、回転軸１５の上偏芯部１５２Ｔに嵌合された上ピストン１２５Ｔが、上シリンダ１２１Ｔの内周面１３７Ｔに沿って公転することにより、上吸入室１３１Ｔが容積を拡大しながら上吸入管１０５から冷媒を吸入し、上圧縮室１３３Ｔが容積を縮小しながら冷媒を圧縮し、圧縮した冷媒の圧力が上吐出弁２００Ｔの外側の上端板カバー室１８０Ｔの圧力より高くなると、上吐出弁２００Ｔが開いて上圧縮室１３３Ｔから上端板カバー室１８０Ｔへ冷媒が吐出される。上端板カバー室１８０Ｔに吐出された冷媒は、上端板カバー１７０Ｔに設けられた円形の上端板カバー吐出孔１７２Ｔ（図１、２参照）から圧縮機筐体１０内に吐出される。 Below, the flow of the refrigerant | coolant by rotation of the rotating shaft 15 is demonstrated. In the upper cylinder chamber 130T, the upper piston 125T fitted to the upper eccentric portion 152T of the rotating shaft 15 revolves along the inner peripheral surface 137T of the upper cylinder 121T by the rotation of the rotating shaft 15. The suction chamber 131T sucks the refrigerant from the upper suction pipe 105 while expanding the volume, and the upper compression chamber 133T compresses the refrigerant while reducing the volume, and the pressure of the compressed refrigerant is the upper end plate cover outside the upper discharge valve 200T. When the pressure in the chamber 180T is higher, the upper discharge valve 200T is opened, and the refrigerant is discharged from the upper compression chamber 133T to the upper end plate cover chamber 180T. The refrigerant discharged into the upper end plate cover chamber 180T is discharged into the compressor housing 10 from a circular upper end plate cover discharge hole 172T (see FIGS. 1 and 2) provided in the upper end plate cover 170T.

また、下シリンダ室１３０Ｓ内において、回転軸１５の回転によって、回転軸１５の下偏芯部１５２Ｓに嵌合された下ピストン１２５Ｓが、下シリンダ１２１Ｓの内周面１３７Ｓに沿って公転することにより、下吸入室１３１Ｓが容積を拡大しながら下吸入管１０４から冷媒を吸入し、下圧縮室１３３Ｓが容積を縮小しながら冷媒を圧縮し、圧縮した冷媒の圧力が下吐出弁２００Ｓの外側の下端板カバー室１８０Ｓの圧力より高くなると、下吐出弁２００Ｓが開いて下圧縮室１３３Ｓから下端板カバー室１８０Ｓへ冷媒が吐出される。下端板カバー室１８０Ｓに吐出された冷媒は、複数の冷媒通路孔１３６及び上端板カバー室１８０Ｔを通って、上端板カバー１７０Ｔの上端板カバー吐出孔１７２Ｔから圧縮機筐体１０内に吐出される。 In the lower cylinder chamber 130S, the lower piston 125S fitted to the lower eccentric portion 152S of the rotating shaft 15 revolves along the inner circumferential surface 137S of the lower cylinder 121S by the rotation of the rotating shaft 15. The lower suction chamber 131S sucks the refrigerant from the lower suction pipe 104 while expanding the volume, and the lower compression chamber 133S compresses the refrigerant while reducing the volume, and the pressure of the compressed refrigerant is the lower end of the outer side of the lower discharge valve 200S. When the pressure is higher than the pressure of the plate cover chamber 180S, the lower discharge valve 200S is opened, and the refrigerant is discharged from the lower compression chamber 133S to the lower end plate cover chamber 180S. The refrigerant discharged into the lower end plate cover chamber 180S is discharged into the compressor housing 10 from the upper end plate cover discharge hole 172T of the upper end plate cover 170T through the plurality of refrigerant passage holes 136 and the upper end plate cover chamber 180T. .

上端板カバー吐出孔１７２Ｔ内には、上端板１６０Ｔの主軸受部１６１Ｔが通されており、上端板カバー室１８０Ｔを通った冷媒が、図１に示すように、上端板カバー吐出孔１７２Ｔの内周面と主軸受部１６１Ｔの外周面との間の隙間Ｇから、圧縮機筐体１０内に吐出される。また、圧縮部１２は、圧縮機筐体１０の下部に収容された潤滑油１８を汲み上げる給油機構（図示せず）を有する。図２に示すように、上端板１６０Ｔの主軸受部１６１Ｔの内周面には、給油機構によって回転軸１５の軸方向の下端側から汲み上げられた潤滑油１８を、主軸受部１６１Ｔ等へ供給する給油溝１６６が形成されている。給油溝１６６は、主軸受部１６１Ｔの軸方向に対して緩やかな螺旋状に形成されている。給油溝１６６は、主軸受部１６１Ｔの下方から主軸受部１６１Ｔの上端まで延びて形成されており、主軸受部１６１Ｔの上端面１６１ａに開口１６６ａを有する（図３参照）。 The main bearing portion 161T of the upper end plate 160T is passed through the upper end plate cover discharge hole 172T, and the refrigerant passing through the upper end plate cover chamber 180T is, as shown in FIG. The fluid is discharged into the compressor housing 10 from the gap G between the circumferential surface and the outer circumferential surface of the main bearing portion 161T. The compression unit 12 also has a refueling mechanism (not shown) that pumps up the lubricating oil 18 housed in the lower part of the compressor housing 10. As shown in FIG. 2, on the inner peripheral surface of the main bearing portion 161T of the upper end plate 160T, the lubricating oil 18 pumped up from the lower end side in the axial direction of the rotating shaft 15 by the oil supply mechanism is supplied to the main bearing portion 161T etc. An oil supply groove 166 is formed. The oil supply groove 166 is formed in a gentle spiral shape in the axial direction of the main bearing portion 161T. The oil supply groove 166 is formed extending from below the main bearing portion 161T to the upper end of the main bearing portion 161T, and has an opening 166a in the upper end surface 161a of the main bearing portion 161T (see FIG. 3).

圧縮機筐体１０内に吐出された冷媒は、ステータ１１１外周に設けられた上下に連通する切欠き（図示せず）、又はステータ１１１の巻線部の隙間（図示せず）、又はステータ１１１とロータ１１２との隙間１１５（図１参照）を通ってモータ１１の上方に導かれ、圧縮機筐体１０の上部に配置された吐出部としての吐出管１０７から吐出される。 The refrigerant discharged into the compressor housing 10 has a notch (not shown) provided on the outer periphery of the stator 111 and communicates with the upper and lower sides, a gap (not shown) of the winding portion of the stator 111, or the stator 111 The air is guided to the upper side of the motor 11 through a gap 115 (see FIG. 1) between the rotor 112 and the rotor 112, and is discharged from a discharge pipe 107 as a discharge part disposed at the top of the compressor housing 10.

（ロータリ圧縮機の特徴的な構成）
次に、実施例のロータリ圧縮機１の特徴的な構成について説明する。本実施例においては、上端板カバー１７０Ｔの上端板カバー吐出孔１７２Ｔと主軸受部１６１Ｔとの間の隙間Ｇが部分的に狭められている点が特徴となる。図３は、実施例のロータリ圧縮機１の上端板カバー１７０Ｔの上端板カバー吐出孔１７２Ｔが有する凸部を示す斜視図である。図４は、実施例のロータリ圧縮機１の上端板カバー１７０Ｔの上端板カバー吐出孔１７２Ｔと主軸受部１６１Ｔとの間の隙間Ｇを上方から見た平面図である。図５は、実施例のロータリ圧縮機１の上端板１６０Ｔの主軸受部１６１Ｔとの間の隙間Ｇを上方から見た平面図である。図６は、実施例のロータリ圧縮機１の上端板カバー１７０Ｔを上方から見た平面図である。 (Characteristic configuration of rotary compressor)
Next, the characteristic configuration of the rotary compressor 1 of the embodiment will be described. The present embodiment is characterized in that the gap G between the upper end plate cover discharge hole 172T of the upper end plate cover 170T and the main bearing portion 161T is partially narrowed. FIG. 3 is a perspective view showing a convex portion of the upper end plate cover discharge hole 172T of the upper end plate cover 170T of the rotary compressor 1 of the embodiment. FIG. 4 is a plan view of a gap G between an upper end plate cover discharge hole 172T of the upper end plate cover 170T of the rotary compressor 1 of the embodiment and the main bearing portion 161T as viewed from above. FIG. 5 is a plan view of the gap G between the main bearing portion 161T of the upper end plate 160T of the rotary compressor 1 of the embodiment as viewed from above. FIG. 6 is a plan view of the upper end plate cover 170T of the rotary compressor 1 of the embodiment as viewed from above.

図３及び図４に示すように、実施例における上端板カバー１７０Ｔには、上端板カバー吐出孔１７２Ｔの周方向にわたって環状の周壁１７７が、主軸受部１６１Ｔの軸方向に沿って延びて形成されている。実施例における上端板カバー１７０Ｔの周壁１７７の上端部には、図５及び図６に示すように、上端板カバー吐出孔１７２Ｔの周方向において給油溝１６６の開口１６６ａに重なる範囲に、主軸受部１６１Ｔの外周面と上端板カバー吐出孔１７２Ｔの内周面との間の隙間Ｇ（図４中の斜線部分）を通過する冷媒を遮る凸部１７８が形成されている。凸部１７８は、給油溝１６６の開口１６６ａから主軸受部１６１Ｔの外周側へ溢れ出る潤滑油１８が、隙間Ｇを通過する冷媒によって飛散されることを抑えるために、上端板カバー吐出孔１７２Ｔの周方向（主軸受部１６１Ｔの周方向）において給油溝１６６の開口１６６ａに重なる範囲に配置されている。凸部１７８は、上端板カバー吐出孔１７２Ｔの周方向における一部に形成されている。凸部１７８は、上端板カバー吐出孔１７２Ｔに形成された周壁１７７の上端部から、主軸受部１６１Ｔの外周面に向かって、上端板カバー吐出孔１７２Ｔの径方向（回転軸１５の径方向）に突出している。 As shown in FIGS. 3 and 4, in the upper end plate cover 170T in the embodiment, an annular peripheral wall 177 is formed extending in the axial direction of the main bearing portion 161T over the circumferential direction of the upper end plate cover discharge hole 172T. ing. In the upper end portion of the peripheral wall 177 of the upper end plate cover 170T in the embodiment, as shown in FIGS. 5 and 6, the main bearing portion in a range overlapping the opening 166a of the oil supply groove 166 in the circumferential direction of the upper end plate cover discharge hole 172T. A convex portion 178 is formed to block the refrigerant passing through a gap G (hatched portion in FIG. 4) between the outer peripheral surface of 161T and the inner peripheral surface of the upper end plate cover discharge hole 172T. The convex portion 178 is used to prevent the lubricating oil 18 overflowing from the opening 166a of the oil supply groove 166 to the outer peripheral side of the main bearing portion 161T from being scattered by the refrigerant passing through the gap G. It is arrange | positioned in the range which overlaps with opening 166a of the oil supply groove 166 in the circumferential direction (circumferential direction of the main bearing part 161T). The convex portion 178 is formed in a part of the upper end plate cover discharge hole 172T in the circumferential direction. The convex portion 178 is a radial direction of the upper end plate cover discharge hole 172T (a radial direction of the rotation shaft 15) from the upper end portion of the peripheral wall 177 formed in the upper end plate cover discharge hole 172T toward the outer peripheral surface of the main bearing portion 161T. Projected into

凸部１７８は、上端板カバー吐出孔１７２Ｔの周方向に対する長さは、主軸受部１６１Ｔの周方向に対する給油溝１６６の幅よりも大きく形成されており、例えば、給油溝１６６の幅が２ｍｍ程度の場合、主軸受部１６１Ｔの周方向における給油溝１６６の両側へ２ｍｍ程度延ばされて、凸部１７８の長さが６ｍｍ程度に形成されることにより、隙間Ｇを通る冷媒の流れを遮ることができる。凸部１７８は、上端板カバー吐出孔１７２Ｔの径方向に突出する突出量は、例えば、１ｍｍ程度であり、突出量が限定されるものではなく、上端板カバー吐出孔１７２Ｔの径方向において１ｍｍ程度をなす隙間Ｇを通る冷媒の流れを遮るものであればよい。また、凸部１７８は、上端板カバー吐出孔１７２Ｔの周壁１７７から、主軸受部１６１Ｔの外周面に当接するように突出して設けられてもよい。なお、実施例では、上端板カバー吐出孔１７２Ｔの周壁１７７の上端から、主軸受部１６１Ｔの上端が、回転軸１５の軸方向に対して突出されており、主軸受部１６１Ｔの上端の突出量が５ｍｍ程度に形成されている。 The convex portion 178 is formed such that the length of the upper end plate cover discharge hole 172T in the circumferential direction is larger than the width of the oil supply groove 166 with respect to the circumferential direction of the main bearing portion 161T. For example, the width of the oil supply groove 166 is about 2 mm. In this case, the flow of the refrigerant passing through the gap G is interrupted by extending about 2 mm to both sides of the oil supply groove 166 in the circumferential direction of the main bearing portion 161T, and forming the length of the convex part 178 to about 6 mm. Can. The amount of protrusion of the convex portion 178 in the radial direction of the upper end plate cover discharge hole 172T is, for example, about 1 mm. The amount of protrusion is not limited. The protrusion 178 is about 1 mm in the radial direction of the upper end plate cover discharge hole 172T. It suffices to interrupt the flow of the refrigerant passing through the gap G which Further, the convex portion 178 may be provided so as to protrude from the peripheral wall 177 of the upper end plate cover discharge hole 172T so as to abut on the outer peripheral surface of the main bearing portion 161T. In the embodiment, the upper end of the main bearing portion 161T protrudes from the upper end of the peripheral wall 177 of the upper end plate cover discharge hole 172T with respect to the axial direction of the rotating shaft 15, and the projection amount of the upper end of the main bearing portion 161T Is formed to about 5 mm.

また、凸部１７８は、上端板カバー吐出孔１７２Ｔの周方向において、図６に示すように、給油溝１６６を中心として給油溝１６６の両側へそれぞれ回転角９０°の範囲を含む回転角１８０°をなす範囲内に形成されればよい。実施例における凸部１７８は、例えば、回転角７５°程度の範囲にわたって形成されている。また、本実施例では、図５に示すように、主軸受部１６１Ｔの給油溝１６６は、主軸受部１６１Ｔの周方向において、上吐出室凹部１６３Ｔ側を向く位置に設けられている。このように給油溝１６６が、上端板カバー吐出孔１７２の周方向において冷媒の流れが相対的に大きい上吐出室凹部１６３Ｔ側に配置された場合であっても、上端板カバー吐出孔１７２Ｔに凸部１７８が設けられたことによって、冷媒による潤滑油１８の飛散が抑えられる。 Further, as shown in FIG. 6, the convex portion 178 has a rotation angle of 180 ° including a range of rotation angles of 90 ° on both sides of the oil feeding groove 166 around the oil feeding groove 166 in the circumferential direction of the upper end plate cover discharge hole 172T. It should just be formed in the range which The convex portion 178 in the embodiment is formed, for example, over a range of about 75 degrees of rotation angle. Further, in the present embodiment, as shown in FIG. 5, the oil supply groove 166 of the main bearing portion 161T is provided at a position facing the upper discharge chamber concave portion 163T in the circumferential direction of the main bearing portion 161T. As described above, even when the oil supply groove 166 is disposed on the upper discharge chamber concave portion 163T side where the flow of refrigerant is relatively large in the circumferential direction of the upper end plate cover discharge hole 172, the upper end plate cover discharge hole 172T is convex. By providing the portion 178, scattering of the lubricating oil 18 by the refrigerant can be suppressed.

また、図４及び図６に示すように、本実施例における凸部１７８は、上端板カバー吐出孔１７２Ｔの周方向における中央（長さ方向の中央）が、回転軸１５の回転方向Ｒの下流側へずらされて形成されている。給油溝１６６を通って主軸受部１６１Ｔの上端面１６１ａの開口１６６ａから溢れ出る潤滑油１８は、主軸受部１６１Ｔ内での回転軸１５の回転による影響を受けて、回転軸１５の回転方向Ｒの下流側へ向かって流れる傾向がある。このため、凸部１７８が、回転軸１５の回転方向Ｒの下流側へ位置がずらされる、すなわち、凸部１７８が、回転軸１５の回転方向Ｒの上流側よりも下流側へ延ばされることにより、主軸受部１６１Ｔの上端面１６１ａの開口１６６ａから溢れ出る潤滑油１８の流れ方向において、潤滑油１８の飛散に影響を及ぼす冷媒の流れが凸部１７８によって効果的に遮られる。このように回転軸１５の回転方向Ｒを考慮することにより、主軸受部１６１Ｔの上端面１６１ａの開口１６６ａから溢れ出る潤滑油１８が、隙間Ｇから吐出される冷媒によって飛散されることが効果的に抑えられる。このように飛散が抑えられることにより、主軸受部１６１Ｔの開口１６６ａから溢れ出る潤滑油１８は、主軸受部１６１Ｔの内周面に沿って広がりながら下方へ流れ落ち、主軸受部１６１Ｔの内周面と回転軸１５の外周面との摺動部分全体へ供給される。 Further, as shown in FIGS. 4 and 6, in the convex portion 178 in the present embodiment, the center (center in the length direction) in the circumferential direction of the upper end plate cover discharge hole 172T is downstream of the rotational direction R of the rotating shaft 15. It is formed to be shifted to the side. The lubricating oil 18 overflowing from the opening 166a of the upper end surface 161a of the main bearing portion 161T through the oil supply groove 166 is affected by the rotation of the rotation shaft 15 in the main bearing portion 161T, and the rotation direction R of the rotation shaft 15 Tends to flow downstream of the For this reason, the position of the convex portion 178 is shifted to the downstream side in the rotational direction R of the rotary shaft 15, that is, the convex portion 178 is extended further downstream than the upstream side of the rotary direction R of the rotary shaft 15. In the flow direction of the lubricating oil 18 overflowing from the opening 166a of the upper end surface 161a of the main bearing portion 161T, the flow of the refrigerant that affects the scattering of the lubricating oil 18 is effectively blocked by the convex portion 178. As described above, by considering the rotational direction R of the rotary shaft 15, it is effective that the lubricating oil 18 overflowing from the opening 166a of the upper end surface 161a of the main bearing portion 161T is scattered by the refrigerant discharged from the gap G. Can be By thus suppressing the scattering, the lubricating oil 18 overflowing from the opening 166a of the main bearing portion 161T flows downward while spreading along the inner peripheral surface of the main bearing portion 161T, and the inner peripheral surface of the main bearing portion 161T , And the entire sliding portion between the outer peripheral surface of the rotating shaft 15 and the other.

なお、本実施例では、凸部１７８が、上端板カバー吐出孔１７２Ｔの周壁１７７の上端部から突出して形成されたが、上端板カバー吐出孔１７２Ｔに周壁１７７を形成することなく上端板カバー吐出孔１７２Ｔの内周面から突出して形成されてもよい。 In the present embodiment, the convex portion 178 is formed to protrude from the upper end portion of the peripheral wall 177 of the upper end plate cover discharge hole 172T, but the upper end plate cover discharge without forming the peripheral wall 177 in the upper end plate cover discharge hole 172T. It may be formed to protrude from the inner circumferential surface of the hole 172T.

上述したように、実施例のロータリ圧縮機１における上端板カバー１７０Ｔの上端板カバー吐出孔１７２Ｔには、上端板カバー吐出孔１７２Ｔの周方向において給油溝１６６の開口１６６ａに重なる範囲に、主軸受部１６１Ｔと上端板カバー吐出孔１７２Ｔとの間の隙間Ｇを通過する冷媒を遮る凸部１７８が形成されている。これにより、給油溝１６６を通って主軸受部１６１Ｔの上端面１６１ａの開口１６６ａから溢れ出た潤滑油１８が、隙間Ｇから吐出される冷媒によって飛散されることが抑えられるので、圧縮機筐体１０内の潤滑油１８がロータリ圧縮機１の外部へ流出することを抑えることができる。このため、ロータリ圧縮機１の内部に収容された潤滑油１８の量が減少することが抑えられ、主軸受部１６１Ｔ等の摺動部分を適正に潤滑することができる。また、ロータリ圧縮機１の外部へ流出した潤滑油１８が、例えば、熱交換器（図示せず）の内部等の冷媒循環回路に付着することが抑えられ、熱交換性能の低下や冷媒循環回路の損傷を抑えることができる。 As described above, in the upper end plate cover discharge hole 172T of the upper end plate cover 170T in the rotary compressor 1 of the embodiment, the main bearing is in a range overlapping the opening 166a of the oil supply groove 166 in the circumferential direction of the upper end plate cover discharge hole 172T. The convex part 178 which interrupts | blocks the refrigerant | coolant which passes the clearance gap G between the part 161T and the upper end plate cover discharge hole 172T is formed. As a result, the lubricating oil 18 overflowing from the opening 166a of the upper end surface 161a of the main bearing portion 161T through the oil supply groove 166 is suppressed from being scattered by the refrigerant discharged from the gap G. The lubricating oil 18 in 10 can be prevented from flowing out of the rotary compressor 1. For this reason, it is possible to suppress the decrease in the amount of the lubricating oil 18 accommodated inside the rotary compressor 1 and to properly lubricate the sliding portion such as the main bearing portion 161T. In addition, the lubricating oil 18 that has flowed out of the rotary compressor 1 is prevented from adhering to the refrigerant circulation circuit such as the inside of a heat exchanger (not shown), for example, and the heat exchange performance decreases or the refrigerant circulation circuit Damage to the

また、実施例では、上端板カバー１７０Ｔが１つの上端板カバー吐出孔１７２Ｔのみを有し、この上端板カバー吐出孔１７２Ｔに主軸受部１６１Ｔが通されているので、上端板カバー室１８０Ｔに吐出されたすべての冷媒が１つの上端板カバー吐出孔１７２Ｔを通って圧縮機筐体１０内に吐出される。このため、特に実施例では、上端板カバー１７０Ｔが、上端板カバー吐出孔１７２Ｔの他に、複数の上端板カバー吐出孔を有する構成に比べて、上端板カバー吐出孔１７２Ｔから吐出される冷媒の勢いが強く、冷媒の吐出量、吐出速度が大きいので、上端板カバー吐出孔１７２Ｔに凸部１７８が設けられたことによる効果が高い。 Further, in the embodiment, since the upper end plate cover 170T has only one upper end plate cover discharge hole 172T, and the main bearing portion 161T passes through the upper end plate cover discharge hole 172T, the discharge is performed in the upper end plate cover chamber 180T. All the collected refrigerant is discharged into the compressor housing 10 through one upper end plate cover discharge hole 172T. For this reason, particularly in the embodiment, compared to the configuration in which the upper end plate cover 170T has a plurality of upper end plate cover discharge holes in addition to the upper end plate cover discharge hole 172T, the refrigerant discharged from the upper end plate cover discharge hole 172T Since the momentum is strong and the discharge amount and discharge speed of the refrigerant are large, the effect obtained by providing the convex portion 178 in the upper end plate cover discharge hole 172T is high.

また、実施例のロータリ圧縮機１における上端板カバー１７０Ｔの凸部１７８は、上端板カバー吐出孔１７２Ｔの周方向において、給油溝１６６の開口１６６ａに対して回転軸１５の回転方向Ｒの下流側に位置がずらされている。これにより、主軸受部１６１Ｔ内での回転軸１５の回転に伴って、潤滑油１８が回転軸１５の回転方向Ｒの下流側へ流れる方向を考慮することで、潤滑油１８を飛散させる冷媒の流れを効果的に遮ることが可能になる。したがって、給油溝１６６を通って主軸受部１６１Ｔの上端面１６１ａの開口１６６ａから溢れ出た潤滑油１８が、隙間Ｇから吐出される冷媒によって飛散されることを効果的に抑えることができる。 Further, the convex portion 178 of the upper end plate cover 170T in the rotary compressor 1 of the embodiment is the downstream side of the rotation direction R of the rotation shaft 15 with respect to the opening 166a of the oil supply groove 166 in the circumferential direction of the upper end plate cover discharge hole 172T. The position is shifted. As a result, by considering the direction in which the lubricating oil 18 flows to the downstream side in the rotational direction R of the rotating shaft 15 with the rotation of the rotating shaft 15 in the main bearing portion 161T, It becomes possible to interrupt the flow effectively. Therefore, the lubricant oil 18 overflowing from the opening 166a of the upper end surface 161a of the main bearing portion 161T through the oil supply groove 166 can be effectively suppressed from being scattered by the refrigerant discharged from the gap G.

また、実施例のロータリ圧縮機１における上端板カバー１７０Ｔの凸部１７８は、主軸受部１６１Ｔに当接して設けられている。これにより、凸部１７８の先端と主軸受部１６１Ｔの外周面との間から冷媒が通過することなく、凸部１７８の位置で冷媒の流れが遮断されるので、凸部１７８によって潤滑油１８の飛散を安定的に抑えることができる。 Further, the convex portion 178 of the upper end plate cover 170T in the rotary compressor 1 of the embodiment is provided in contact with the main bearing portion 161T. As a result, the refrigerant does not flow from between the tip of the convex portion 178 and the outer peripheral surface of the main bearing portion 161T, and the flow of the refrigerant is blocked at the position of the convex portion 178. Scattering can be stably suppressed.

以下、他の実施例のロータリ圧縮機及びその変形例１、２について図面を参照して説明する。他の実施例及びその変形例１、２は、上端板カバー吐出孔１７２Ｔと主軸受部１６１Ｔとの間の隙間Ｇの周方向における一部を狭める構造が、上述した実施例と異なる。便宜上、他の実施例及びその変形例１、２においても、実施例と同一の構成部材には実施例と同一の符号を付して説明を省略する。
（他の実施例） Hereinafter, a rotary compressor of another embodiment and its modification examples 1 and 2 will be described with reference to the drawings. The other embodiment and the first and second modifications thereof are different from the above-described embodiment in the structure for narrowing a part of the gap G between the upper end plate cover discharge hole 172T and the main bearing portion 161T in the circumferential direction. For convenience, in the other embodiments and the first and second modifications thereof, the same components as those of the embodiments are denoted by the same reference numerals as those of the embodiments, and the description thereof will be omitted.
(Other embodiments)

図７は、他の実施例のロータリ圧縮機の上端板カバー１７０Ｔの上端板カバー吐出孔と主軸受部１６１Ｔとの間の隙間Ｇを上方から見た平面図である。図８は、他の実施例のロータリ圧縮機の上端板カバー１７０Ｔを上方から見た平面図である。 FIG. 7 is a plan view of a gap G between an upper end plate cover discharge hole of the upper end plate cover 170T of the rotary compressor of another embodiment and the main bearing portion 161T as viewed from above. FIG. 8 is a plan view of the upper end plate cover 170T of the rotary compressor of another embodiment as viewed from above.

図７及び図８に示すように、回転軸１５の軸方向に直交する平面上において、上端板カバー１７０Ｔの上端板カバー吐出孔１７２Ｔ−１は、回転軸１５の径方向における中心Ｏ１（主軸受部１６１Ｔの径方向における中心）に対して、上端板カバー吐出孔１７２Ｔ−１の中心Ｏ２が、給油溝１６６の開口１６６ａ側から遠ざかる方向へ偏心して形成されている。言い換えると、回転軸１５の中心Ｏ１は、上端板カバー吐出孔１７２Ｔ−１の中心Ｏ２に対して、給油溝１６６側へ近づく方向へ偏心して配置されている。また、回転軸１５の軸方向に直交する平面上において、回転軸１５の中心Ｏ１に対して上端板カバー吐出孔１７２Ｔ−１の中心Ｏ２が偏心する方向、すなわち、中心Ｏ１と中心Ｏ２を結ぶ方向は、例えば、主軸受部１６１Ｔの上端面１６１ａに開口した給油溝１６６の開口１６６ａを通過する方向を向いている。 As shown in FIGS. 7 and 8, on the plane orthogonal to the axial direction of the rotation shaft 15, the upper end plate cover discharge hole 172T-1 of the upper end plate cover 170T has a center O1 in the radial direction of the rotation shaft 15 (main bearing The center O2 of the upper end plate cover discharge hole 172T-1 is eccentrically formed in a direction away from the opening 166a side of the oil supply groove 166 with respect to the center in the radial direction of the portion 161T. In other words, the center O1 of the rotary shaft 15 is eccentrically disposed in the direction approaching the oil supply groove 166 with respect to the center O2 of the upper end plate cover discharge hole 172T-1. Further, on a plane orthogonal to the axial direction of the rotation shaft 15, a direction in which the center O2 of the upper end plate cover discharge hole 172T-1 is eccentric to the center O1 of the rotation shaft 15, that is, a direction connecting the center O1 and the center O2. For example, it faces the direction of passing through the opening 166a of the oil supply groove 166 opened in the upper end surface 161a of the main bearing portion 161T.

このため、上端板カバー吐出孔１７２Ｔ−１内に通された主軸受部１６１Ｔは、給油溝１６６側へ近づいて配置されており、上端板カバー吐出孔１７２Ｔ−１の内周面と主軸受部１６１Ｔの外周面との間の隙間Ｇが、上端板カバー吐出孔１７２Ｔ−１の周方向において、給油溝１６６側へ近づくに従って小さくなると共に、給油溝１６６と反対側へ近づくに従って大きくなるように形成されている。なお、主軸受部１６１Ｔの外周面は、給油溝１６６側において、上端板カバー吐出孔１７２Ｔ−１の周壁１７７に接するように配置されてもよい。 Therefore, the main bearing portion 161T passed through the upper end plate cover discharge hole 172T-1 is disposed closer to the oil supply groove 166 side, and the inner peripheral surface of the upper end plate cover discharge hole 172T-1 and the main bearing portion The gap G between the outer peripheral surface of 161T and the outer peripheral surface of the upper end plate cover discharge hole 172T-1 becomes smaller as it gets closer to the oil supply groove 166 in the circumferential direction, and becomes larger as it gets closer to the oil supply groove 166 It is done. The outer peripheral surface of the main bearing portion 161T may be disposed in contact with the peripheral wall 177 of the upper end plate cover discharge hole 172T-1 on the side of the oil supply groove 166.

また、本実施例では、回転軸１５の中心Ｏ１に対して上端板カバー吐出孔１７２Ｔ−１の中心Ｏ２が偏心されているが、上端板カバー吐出孔１７２Ｔ−１から吐出される冷媒の吐出状態が、上述の中心Ｏ１と中心Ｏ２とが一致するもの（偏心がないもの）と比べて変化しないように、回転軸１５の軸方向に直交する平面上において隙間Ｇ（図７中の斜線部分）全体が占める開口面積が、偏心がないものと同等に確保されている。 Further, in the present embodiment, the center O2 of the upper end plate cover discharge hole 172T-1 is eccentric to the center O1 of the rotary shaft 15, but the discharge state of the refrigerant discharged from the upper end plate cover discharge hole 172T-1 However, the gap G (hatched portion in FIG. 7) on the plane orthogonal to the axial direction of the rotation shaft 15 so that it does not change as compared with that in which the above center O1 and center O2 coincide (no eccentricity). The opening area occupied by the whole is secured equal to that without eccentricity.

他の実施例によれば、回転軸１５の中心Ｏ１に対して上端板カバー吐出孔１７２Ｔ−１の中心Ｏ２が偏心されることにより、上述した実施例と同様に、上端板カバー吐出孔１７２Ｔ−１と主軸受部１６１Ｔとの間の、給油溝１６６の開口１６６ａ側の隙間Ｇが狭められる。このため、他の実施例によれば、実施例のように凸部１７８を形成することなく、比較的に簡素な構成により、隙間Ｇの周方向における一部を狭めることができる。 According to another embodiment, the center O2 of the upper end plate cover discharge hole 172T-1 is eccentric with respect to the center O1 of the rotating shaft 15, so that the upper end plate cover discharge hole 172T- is similar to the embodiment described above. A gap G between the opening 166a of the oil supply groove 166 and the main bearing portion 161T is narrowed. For this reason, according to another embodiment, it is possible to narrow a part of the gap G in the circumferential direction with a relatively simple configuration without forming the convex portion 178 as in the embodiment.

また、他の実施例においても、上述した実施例と同様に、給油溝１６６を通って主軸受部１６１Ｔの上端面１６１ａの開口１６６ａから溢れ出た潤滑油１８が、隙間Ｇから吐出される冷媒によって飛散されることが抑えられ、圧縮機筐体１０内の潤滑油１８がロータリ圧縮機１の外部へ流出することを抑えることができる。その結果、ロータリ圧縮機１の内部に収容された潤滑油１８の減少が抑えられ、主軸受部１６１Ｔ等の摺動部分を適正に潤滑することができる。また、ロータリ圧縮機１の外部へ流出した潤滑油１８によって冷媒循環回路の性能低下や損傷が生じることを抑えることができる。 Also, in the other embodiments, as in the above-described embodiment, the lubricating oil 18 overflowing from the opening 166a of the upper end surface 161a of the main bearing portion 161T through the oil supply groove 166 is the refrigerant discharged from the gap G As a result, scattering of the lubricant oil 18 in the compressor housing 10 can be suppressed from flowing out of the rotary compressor 1. As a result, the reduction of the lubricating oil 18 accommodated inside the rotary compressor 1 can be suppressed, and the sliding portion such as the main bearing portion 161T can be properly lubricated. Further, it is possible to suppress the performance deterioration and damage of the refrigerant circuit by the lubricating oil 18 that has flowed out of the rotary compressor 1.

図９は、他の実施例のロータリ圧縮機の変形例１としての、上端板カバー吐出孔１７２Ｔ−１と主軸受部１６１Ｔとの間の隙間Ｇを上方から見た拡大平面図である。図１０は、他の実施例のロータリ圧縮機の変形例２としての、上端板カバー吐出孔１７２Ｔ−１と主軸受部１６１Ｔとの間の隙間Ｇを上方から見た拡大平面図である。 FIG. 9 is an enlarged plan view of the gap G between the upper end plate cover discharge hole 172T-1 and the main bearing portion 161T as a first modification of the rotary compressor according to the other embodiment as viewed from above. FIG. 10 is an enlarged plan view of the gap G between the upper end plate cover discharge hole 172T-1 and the main bearing portion 161T as a modification 2 of the rotary compressor of another embodiment, viewed from the upper side.

回転軸１５の軸方向に直交する平面上において、回転軸１５の中心Ｏ１に対して上端板カバー吐出孔１７２Ｔ−１の中心Ｏ２が偏心する方向（中心Ｏ１と中心Ｏ２を結ぶ方向）は、給油溝１６６の開口１６６ａを通過する方向に限定されるものではなく、図９に示す変形例１のように、開口１６６ａに対する回転軸１５の回転方向Ｒの下流側へ、中心Ｏ２まわりに回転させた方向へ向きがずらされてもよい。 The direction in which the center O2 of the upper end plate cover discharge hole 172T-1 is eccentric to the center O1 of the rotation shaft 15 on the plane orthogonal to the axial direction of the rotation shaft 15 (the direction connecting the center O1 and the center O2) It is not limited to the direction of passing through the opening 166a of the groove 166, and it is rotated around the center O2 to the downstream side of the rotational direction R of the rotating shaft 15 with respect to the opening 166a as in the first modification shown in FIG. The direction may be offset.

上述したように、給油溝１６６を通って開口１６６ａを経て主軸受部１６１Ｔの上端面１６１ａから溢れ出る潤滑油１８は、回転軸１５の回転の影響により、回転軸１５の回転方向Ｒの下流側へ向かって流れる傾向がある。このため、上端板カバー吐出孔１７２Ｔ−１の中心Ｏ２が偏心する方向が、回転軸１５の回転方向Ｒの下流側へ位置がずらされることにより、主軸受部１６１Ｔの上端面１６１ａの開口１６６ａから溢れ出る潤滑油１８の流れ方向において隙間Ｇが狭められるので、潤滑油１８の飛散に影響を及ぼす冷媒の流れが効果的に遮ることができる。このように回転軸１５の回転方向Ｒを考慮することにより、主軸受部１６１Ｔの上端面１６１ａの開口１６６ａから溢れ出る潤滑油１８が、隙間Ｇから吐出される冷媒によって飛散されることを効果的に抑えることができる。 As described above, the lubricating oil 18 overflowing from the upper end surface 161a of the main bearing portion 161T through the oil supply groove 166 and the opening 166a is the downstream side of the rotation direction R of the rotation shaft 15 under the influence of the rotation of the rotation shaft 15. It tends to flow toward the For this reason, the direction in which the center O2 of the upper end plate cover discharge hole 172T-1 is eccentric is shifted to the downstream side in the rotational direction R of the rotating shaft 15, thereby making the opening 166a of the upper end surface 161a of the main bearing portion 161T. Since the gap G is narrowed in the flow direction of the lubricating oil 18 that overflows, the flow of the refrigerant that affects the scattering of the lubricating oil 18 can be effectively blocked. As described above, by considering the rotational direction R of the rotary shaft 15, it is effective that the lubricating oil 18 overflowing from the opening 166a of the upper end surface 161a of the main bearing portion 161T is scattered by the refrigerant discharged from the gap G. Can be reduced to

また、図１０に示す変形例２のように、回転軸１５の軸方向に直交する平面上において、回転軸１５の中心Ｏ１に対して上端板カバー吐出孔１７２Ｔ−１の中心Ｏ２が、給油溝１６６の開口１６６ａ側から遠ざかる方向へ偏心されると共に、上端板カバー吐出孔１７２Ｔ−１の周方向において給油溝１６６の開口１６６ａに重なる範囲に凸部１７８が形成されてもよい。また、回転軸１５の軸方向に直交する平面上において、回転軸１５の中心Ｏ１と上端板カバー吐出孔１７２Ｔ−１の中心Ｏ２とを結ぶ方向は、給油溝１６６の開口１６６ａを通過している。 Further, as in the second modification shown in FIG. 10, on the plane orthogonal to the axial direction of the rotary shaft 15, the center O2 of the upper end plate cover discharge hole 172T-1 with respect to the center O1 of the rotary shaft 15 is an oil supply groove. The convex portion 178 may be formed in a range which is eccentric in a direction away from the opening 166a side of the 166 and overlaps the opening 166a of the oil supply groove 166 in the circumferential direction of the upper end plate cover discharge hole 172T-1. Further, on a plane orthogonal to the axial direction of the rotary shaft 15, the direction connecting the center O1 of the rotary shaft 15 and the center O2 of the upper end plate cover discharge hole 172T-1 passes through the opening 166a of the oil supply groove 166 .

変形例２によれば、上述した実施例、他の実施例と比べて、凸部１７８の突出量、上端板カバー吐出孔１７２Ｔ−１の中心Ｏ２の偏心量を小さく形成することができる。また、変形例２によれば、実施例のように凸部１７８の突出量のみで隙間Ｇを狭める構成に比べて、上端板カバー吐出孔１７２Ｔ−１の周方向の広範囲にわたって隙間Ｇを狭めることができる。このため、変形例２は、実施例と比べ、給油溝１６６側の隙間Ｇから吐出される冷媒を更に減らし、主軸受部１６１Ｔの上端面１６１ａの開口１６６ａから溢れ出る潤滑油１８が、隙間Ｇから吐出される冷媒によって飛散されることを更に抑えることができる。 According to the second modification, the amount of protrusion of the convex portion 178 and the amount of eccentricity of the center O2 of the upper end plate cover discharge hole 172T-1 can be smaller than those of the above-described embodiment and the other embodiments. Further, according to the second modification, the gap G is narrowed over a wide range in the circumferential direction of the upper end plate cover discharge hole 172T-1 as compared with the configuration in which the gap G is narrowed only by the protrusion amount of the convex portion 178 as in the embodiment. Can. For this reason, the second modification further reduces the refrigerant discharged from the gap G on the oil supply groove 166 side as compared with the embodiment, and the lubricating oil 18 overflowing from the opening 166a of the upper end surface 161a of the main bearing portion 161T is the gap G. It can further suppress scattering by the refrigerant discharged from the nozzle.

なお、実施例では、２シリンダ型のロータリ圧縮機に適用された場合を説明したが、２シリンダ型に限定されるものではなく、１シリンダ型のロータリ圧縮機に適用されてもよい。上端板カバー吐出孔１７２Ｔと主軸受部１６１Ｔとの間の隙間Ｇの周方向における冷媒の吐出速度や吐出量は、上端板カバー室１８０Ｔ内の上吐出孔１９０Ｔの位置等によっても差が生じる。このため、隙間Ｇから吐出される冷媒による潤滑油１８の飛散を抑える観点では、給油溝１６６の位置を、隙間Ｇの周方向において冷媒の吐出速度等が相対的に小さい位置に配置することも考えられる。しかし、２シリンダ型のロータリ圧縮機１では、上端板カバー室１８０Ｔ内に、上吐出孔１９０Ｔと、複数の冷媒通路孔１３６とが配置されているので（図５参照）、隙間Ｇの周方向において、冷媒の吐出量、吐出速度が相対的に大きくなる上吐出孔１９０Ｔに近い位置と、複数の冷媒通路孔１３６に近い位置を避けるように給油溝１６６の開口１６６ａを配置する場合、構造上の制約が大きい。このように、２シリンダ型のロータリ圧縮機１では、上端板カバー室１８０Ｔ内に上吐出孔１９０Ｔのみが配置されている１シリンダ型のロータリ圧縮機に比べて、給油溝１６６の開口１６６ａの配置によって潤滑油１８の飛散を抑えることが難しいので、本実施例における凸部１７８によって冷媒を遮る構成が有効である。 In the embodiment, the case where the invention is applied to a two-cylinder rotary compressor has been described. However, the invention is not limited to the two-cylinder rotary compressor, and may be applied to a one-cylinder rotary compressor. The discharge speed and discharge amount of the refrigerant in the circumferential direction of the gap G between the upper end plate cover discharge hole 172T and the main bearing portion 161T also differ depending on the position and the like of the upper discharge hole 190T in the upper end plate cover chamber 180T. Therefore, from the viewpoint of suppressing the scattering of the lubricating oil 18 by the refrigerant discharged from the gap G, the position of the oil supply groove 166 may be arranged at a position where the discharge speed of the refrigerant is relatively small in the circumferential direction of the gap G. Conceivable. However, in the two-cylinder rotary compressor 1, since the upper discharge hole 190T and the plurality of refrigerant passage holes 136 are disposed in the upper end plate cover chamber 180T (see FIG. 5), the circumferential direction of the gap G is When the opening 166a of the oil supply groove 166 is arranged so as to avoid the position near the upper discharge hole 190T where the discharge amount and discharge speed of the refrigerant become relatively large and the position near the plurality of refrigerant passage holes 136 The restriction of As described above, in the two-cylinder rotary compressor 1, the arrangement of the opening 166a of the oil supply groove 166 as compared with the one-cylinder rotary compressor in which only the upper discharge hole 190T is disposed in the upper end plate cover chamber 180T. Since it is difficult to suppress the scattering of the lubricating oil 18 by this, the configuration in which the refrigerant is blocked by the convex portion 178 in this embodiment is effective.

以上、実施例を説明したが、上述した内容により実施例が限定されるものではない。また、上述した構成要素には、当業者が容易に想定できるもの、実質的に同一のもの、いわゆる均等の範囲のものが含まれる。さらに、上述した構成要素は適宜組み合わせることが可能である。さらに、実施例の要旨を逸脱しない範囲で構成要素の種々の省略、置換及び変更のうち少なくとも１つを行うことができる。 As mentioned above, although an Example was described, an Example is not limited by the content mentioned above. In addition, the above-mentioned constituent elements include those which can be easily conceived by those skilled in the art, substantially the same ones, and so-called equivalent ranges. Furthermore, the components described above can be combined as appropriate. Furthermore, at least one of various omissions, substitutions, and modifications of the components can be made without departing from the scope of the embodiments.

１ロータリ圧縮機
１０圧縮機筐体
１１モータ
１２圧縮部
１５回転軸
１８潤滑油
１０４下吸入管（吸入部）
１０５上吸入管（吸入部）
１０７吐出管（吐出部）
１３３Ｔ上圧縮室（圧縮室）
１３３Ｓ下圧縮室（圧縮室）
１６０Ｔ上端板
１６１Ｔ主軸受部（軸受部）
１６１ａ上端面
１６６給油溝
１６６ａ開口
１７０Ｔ上端板カバー
１７２Ｔ上端板カバー吐出孔
１７８凸部
１８０Ｔ上端板カバー室
１９０Ｔ上吐出孔（吐出孔）
Ｇ隙間
Ｏ１、Ｏ２中心
Ｒ回転方向 DESCRIPTION OF SYMBOLS 1 rotary compressor 10 compressor housing 11 motor 12 compression part 15 rotating shaft 18 lubricating oil 104 lower suction pipe (suction part)
105 Upper suction pipe (suction part)
107 Discharge pipe (discharge part)
133T upper compression chamber (compression chamber)
133S Lower compression chamber (compression chamber)
160T upper end plate 161T main bearing (bearing)
161a upper end surface 166 oil supply groove 166a opening 170T upper end plate cover 172T upper end plate cover discharge hole 178 convex portion 180T upper end plate cover chamber 190T upper discharge hole (discharge hole)
G gap O1, O2 center R rotation direction

Claims

A vertically disposed cylindrical compressor housing provided with a refrigerant discharge part at the upper part and a suction part for the refrigerant provided at the lower part, and the refrigerant drawn from the suction part disposed at the lower part of the compressor housing , And a motor for driving the compression unit, which is disposed on the upper portion of the compressor casing, and which compresses the ink and discharges it from the discharge unit.
The compression unit is
An annular cylinder forming a compression chamber, an upper end plate closing the upper side of the cylinder, a rotary shaft supported by a bearing provided on the upper end plate and rotated by the motor, and covering the upper end plate to cover the upper end plate An upper end plate cover forming an upper end plate cover chamber between the upper end plate, an upper end plate cover discharge hole provided in the upper end plate cover and communicating the upper end plate cover chamber with the inside of the compressor housing; A discharge hole provided in the upper end plate for communicating the compression chamber with the upper end plate cover chamber;
In a rotary compressor having
The compressor housing contains lubricating oil for lubricating the compression unit.
On the inner peripheral surface of the bearing portion, there is formed an oil supply groove extending from the lower side in the axial direction of the rotary shaft to the upper end surface of the bearing portion and having an opening at the upper end surface to supply the lubricating oil to the bearing portion And
The bearing portion of the upper end plate is passed through the upper end plate cover discharge hole of the upper end plate cover, and the bearing portion and the upper end plate cover are in a range overlapping the opening in the circumferential direction of the upper end plate cover discharge hole. The convex part which interrupts | blocks the refrigerant | coolant which passes the clearance gap between discharge holes is formed,
Rotary compressor.

The convex portion is shifted in the circumferential direction of the upper end plate cover discharge hole to the downstream side of the rotation direction of the rotation shaft with respect to the opening.
The rotary compressor according to claim 1.

The convex portion is provided in contact with the bearing portion.
The rotary compressor according to claim 1.

The center of the upper end plate cover discharge hole is eccentric in a direction away from the opening side with respect to the center of the rotation axis on a plane orthogonal to the axial direction of the rotation axis.
The rotary compressor according to any one of claims 1 to 3.

A vertically disposed cylindrical compressor housing provided with a refrigerant discharge part at the upper part and a suction part for the refrigerant provided at the lower part, and the refrigerant drawn from the suction part disposed at the lower part of the compressor housing , And a motor for driving the compression unit, which is disposed on the upper portion of the compressor casing, and which compresses the ink and discharges it from the discharge unit.
The compression unit is
An annular cylinder forming a compression chamber, an upper end plate closing the upper side of the cylinder, a rotary shaft supported by a bearing provided on the upper end plate and rotated by the motor, and covering the upper end plate to cover the upper end plate An upper end plate cover forming an upper end plate cover chamber between the upper end plate, an upper end plate cover discharge hole provided in the upper end plate cover and communicating the upper end plate cover chamber with the inside of the compressor housing; A discharge hole provided in the upper end plate for communicating the compression chamber with the upper end plate cover chamber;
In a rotary compressor having
The compressor housing contains lubricating oil for lubricating the compression unit.
On the inner peripheral surface of the bearing portion, there is formed an oil supply groove extending from the lower side in the axial direction of the rotary shaft to the upper end surface of the bearing portion and having an opening at the upper end surface to supply the lubricating oil to the bearing portion And
The bearing portion of the upper end plate is passed through the upper end plate cover discharge hole of the upper end plate cover;
The rotary compressor, wherein a center of the upper end plate cover discharge hole is eccentric with respect to a center of the rotation axis in a direction away from the opening on a plane orthogonal to the axial direction of the rotation axis.

The direction in which the center of the upper end plate cover discharge hole is eccentric to the center of the rotation axis is the downstream side of the rotational direction of the rotation shaft with respect to the opening in the circumferential direction of the upper end plate cover discharge hole Are staggered,
The rotary compressor according to claim 5.