JPH09158863A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve oil supply ability in a scroll compressor in which a first back pressure chamber which is communicated with a bearing part and retains pressure approximately equal to discharge pressure and a second back pressure chamber which retains low pressure are formed, by arranging an oil discharging passage which runs in only one direction in which lubricant oil supplied to a bearing part is introduced to a lubricant oil part. SOLUTION: When a crankshaft is rotated by an electric motor so that a scroll compressor is driven, centrifugal pump action is simultaneously acted by an oil supply passage 22 eccentrically arranged to the crankshaft so that lubricant oil is guided upward the oil supply passage 22 and reaches a bearing part by being passed through an oil supply passage 22b and a space at the upper end of the crankshaft. Circulating oil which is circulated in a turning bearing part 30 from a pressure difference oil supply passage through an oil supply groove 30a from the space at the upper end of the crankshaft and has lubricated the turning bearing part 30, reaches a first back pressure chamber 99, and next is introduced from an oil discharge hole to an oil discharge pipe 20. Hereat, lubricant oil pressure is raised more than discharge pressure so that the valve 201 of the oil discharge pipe 20 is opened by differential pressure, therefore the lubricant oil is discharged to the inside of a sealed container.

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【発明の属する技術分野】本発明は冷凍，空調用の冷媒
圧縮機，空気やその他のガス圧縮機として好適なスクロ
ール圧縮機に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor suitable as a refrigerant compressor for refrigeration and air conditioning, and a compressor for air and other gases.

【０００２】[0002]

【従来の技術】旋回スクロールと固定スクロールを備
え、旋回スクロールの背面側のシール部材により中央部
の軸受部を吐出圧力に保持したスクロール圧縮機におい
て、シール部材に絞り通路を備えた構造は特願平5−127
088 号明細書に記載されている。2. Description of the Related Art In a scroll compressor having an orbiting scroll and a fixed scroll, in which a central bearing portion is kept at a discharge pressure by a sealing member on the back side of the orbiting scroll, a structure having a throttle passage in the sealing member is a patent application. Flat 5-127
No. 088.

【０００３】また、旋回スクロールと固定スクロールを
備え、旋回スクロールの背面側のシール部材により中央
部の軸受部を吐出圧力に保持したスクロール圧縮機の給
油構造としては特開昭60−224988号公報に記載されてい
る。この構造は密閉容器内を吐出圧力とし、クランク軸
および各軸受部を吐出圧力の雰囲気内に設置し、クラン
ク軸に設けた偏芯孔の遠心ポンプ作用にて各軸受部を給
油するもので、各軸受部を給油した後の潤滑油は排油通
路を経て潤滑油部へ戻し密閉容器内の吐出圧力下を循環
させる。Japanese Patent Laid-Open Publication No. 60-224988 discloses an oil supply structure for a scroll compressor which includes an orbiting scroll and a fixed scroll, and a bearing member at the center of the orbiting scroll is held at a discharge pressure by a seal member on the back side of the orbiting scroll. Have been described. In this structure, the discharge pressure is in the closed container, the crankshaft and each bearing are installed in the atmosphere of discharge pressure, and each bearing is oiled by the centrifugal pump action of the eccentric hole provided in the crankshaft. Lubricating oil after replenishing each bearing portion is returned to the lubricating oil portion through the oil discharge passage and circulates under the discharge pressure in the closed container.

【０００４】[0004]

【発明が解決しようとする課題】シール部材に絞り通路
を備えた従来のスクロール圧縮機の場合、軸受部に給油
された潤滑油はすべて第２の背圧室を経て圧縮室へ流入
するため、圧縮機の入力を増大させる問題があった。ま
た、圧縮室に流入した潤滑油は冷媒ガスと混合して密閉
容器内に吐出されるので、冷媒ガスとともに機外に流出
しやすいという問題があった。In the case of the conventional scroll compressor having the sealing member provided with the throttle passage, all the lubricating oil supplied to the bearing portion flows into the compression chamber through the second back pressure chamber. There was a problem of increasing the input of the compressor. Further, since the lubricating oil that has flowed into the compression chamber is mixed with the refrigerant gas and discharged into the closed container, there is a problem that it tends to flow out of the machine together with the refrigerant gas.

【０００５】一方、遠心ポンプ及び排油通路を備えた従
来のスクロール圧縮機の場合、低速運転時に十分な給油
量が得られないという問題があり、低速側の運転領域を
制限していた。低速運転時に給油量を確保するには、シ
ール部材に絞り通路を設け、第１の背圧室と第２の背圧
室の差圧により潤滑油を導く構造が有効であるが、排油
通路が常時吐出ガス雰囲気に解放されている従来のスク
ロール圧縮機では、排油通路を介して吐出ガスが流れ込
み給油を阻害するため採用することができなかった。ま
た、シール部材に絞り通路を設けない場合でも、シール
部の漏れがあると同様に吐出ガスが流れこみ給油を阻害
する恐れがあった。On the other hand, in the case of the conventional scroll compressor having the centrifugal pump and the oil drain passage, there is a problem that a sufficient amount of oil cannot be obtained at low speed operation, and the operation area on the low speed side is limited. In order to secure the amount of oil supply at low speed operation, it is effective to provide a throttle passage in the seal member and guide the lubricating oil by the differential pressure between the first back pressure chamber and the second back pressure chamber. However, the conventional scroll compressor, which is always open to the discharge gas atmosphere, cannot be used because the discharge gas flows in through the oil discharge passage and obstructs oil supply. Even when the throttle member is not provided in the seal member, if the seal portion leaks, the discharge gas may flow in and obstruct the oil supply.

【０００６】本発明の目的は、給油能力の向上を図り、
可変速仕様の低速時でも軸受部の給油を可能とする構造
を提供することにある。An object of the present invention is to improve refueling capacity,
An object of the present invention is to provide a structure capable of refueling a bearing portion even at a low speed of variable speed specifications.

【０００７】[0007]

【課題を解決するための手段】スクロール圧縮機機構を
密閉容器内に納め、密閉容器内を吐出圧力に維持し、旋
回スクロールの背面に複数の背圧室を形成する。背圧室
間に少なくとも一つのシール部材を設けることにより、
中央部の軸受部と連通する第１の背圧室と外側の第２の
背圧室とを構成する。このため第１の背圧室および軸受
部はほぼ吐出圧力に等しい圧力となる。また、シール部
材外側の第２の背圧室は圧縮室に連通する中間孔によっ
て吸入圧力と吐出圧力の中間の圧力に、あるいは吸入室
に連通することにより吸入圧力に維持される。A scroll compressor mechanism is housed in a closed container, the inside of the closed container is maintained at a discharge pressure, and a plurality of back pressure chambers are formed on the back surface of an orbiting scroll. By providing at least one seal member between the back pressure chambers,
A first back pressure chamber and an outer second back pressure chamber that communicate with the central bearing portion are formed. Therefore, the first back pressure chamber and the bearing portion have a pressure substantially equal to the discharge pressure. Further, the second back pressure chamber on the outer side of the seal member is maintained at the intermediate pressure between the suction pressure and the discharge pressure by the intermediate hole communicating with the compression chamber or maintained at the suction pressure by communicating with the suction chamber.

【０００８】スクロール圧縮機で、クランク軸内に潤滑
油部と軸受部を連通する遠心ポンプを備えた給油通路を
設ける。また、軸受部に給油された潤滑油を潤滑油へ導
くように密閉容器内の吐出圧力雰囲気に連通する排油通
路を設け、遠心ポンプによる給油圧で軸受部の圧力が密
閉容器内の吐出圧力より高い状態時のみ排油通路が開通
するように排油通路の途中または開口部に弁を設ける。
更に、第１の背圧室と第２の背圧室の間に給油通路及び
排油通路に対して十分に通路面積を絞った絞り通路を設
ける。絞り通路はシール部材に設けてもシール部材に接
する部材に設けてもどちらでも良い。In a scroll compressor, an oil supply passage provided with a centrifugal pump that connects a lubricating oil portion and a bearing portion is provided in the crankshaft. In addition, an exhaust oil passage that communicates with the discharge pressure atmosphere in the closed container is provided to guide the lubricating oil supplied to the bearing to the lubricating oil. A valve is provided in the middle of the oil drain passage or in the opening so that the oil drain passage is opened only in a higher state.
Further, a throttle passage whose passage area is sufficiently narrowed with respect to the oil supply passage and the oil discharge passage is provided between the first back pressure chamber and the second back pressure chamber. The throttle passage may be provided either in the seal member or in a member in contact with the seal member.

【０００９】また、第１の背圧室および第２の背圧室は
それぞれ複数の空間にもって構成されていても差支えな
く、第２の背圧室は吐出圧力より低い圧力であれば複数
の異なる圧力の空間で構成される場合もある。Further, the first back pressure chamber and the second back pressure chamber may have a plurality of spaces, and the second back pressure chamber may have a plurality of spaces as long as the pressure is lower than the discharge pressure. It may be composed of spaces with different pressures.

【００１０】このように給油通路，弁を備えた排油通
路，絞り通路を構成したスクロール圧縮機では、遠心ポ
ンプ作用と差圧の両方を利用して軸受部に給油すること
が可能となる。遠心ポンプ作用は給油通路を回転軸に対
して偏芯した設けたクランク軸が回転することにより働
く。また、差圧は第１の背圧室と第２の背圧室の間の差
圧であり、絞り通路を介して潤滑油を第２の背圧室へ流
すことにより軸受部に潤滑油が導かれる。絞り通路を設
けない構造でも、シール部に漏れが生じる場合は同様の
作用が働く。In the scroll compressor having the oil supply passage, the oil discharge passage provided with the valve, and the throttle passage as described above, it is possible to supply oil to the bearing portion by utilizing both the centrifugal pump action and the differential pressure. The centrifugal pump action works by rotating a crankshaft provided with the oil supply passage eccentric with respect to the rotation shaft. Further, the differential pressure is a differential pressure between the first back pressure chamber and the second back pressure chamber, and the lubricating oil is made to flow through the throttle passage to the second back pressure chamber so that the lubricating oil is applied to the bearing portion. Be guided. Even in the structure in which the throttle passage is not provided, the same action works when the seal portion leaks.

【００１１】遠心ポンプで十分に給油量を確保できる運
転域では、吐出圧力下の潤滑油部の潤滑油を遠心ポンプ
作用で軸受部に給油すると同時に差圧によってもまた給
油される。この際には、軸受部は遠心ポンプの給油圧で
密閉室内の吐出圧力より高い圧力となっているため、排
油通路に設けられた弁が解放状態となり遠心ポンプ作用
で軸受部に給油された潤滑油は排油通路を介して密閉容
器内に排出され潤滑油部に還流する。差圧により第２の
背圧室に導かれた潤滑油は中間孔あるいは吸入室に連通
する通路を通って圧縮室に入り、冷媒ガスと共に密閉容
器内に吐出され潤滑油部に戻る。In the operating range where the centrifugal pump can secure a sufficient amount of oil supply, the lubricating oil of the lubricating oil portion under the discharge pressure is supplied to the bearing portion by the action of the centrifugal pump, and at the same time, the lubricating oil is also fed by the differential pressure. At this time, since the bearing has a pressure higher than the discharge pressure in the sealed chamber due to the oil pressure supplied by the centrifugal pump, the valve provided in the oil discharge passage is opened and the bearing is oiled by the centrifugal pump action. The lubricating oil is discharged into the closed container via the oil discharge passage and flows back to the lubricating oil portion. The lubricating oil guided to the second back pressure chamber by the differential pressure enters the compression chamber through the intermediate hole or the passage communicating with the suction chamber, is discharged into the closed container together with the refrigerant gas, and returns to the lubricating oil portion.

【００１２】一方、低速運転時には、遠心ポンプ作用に
よる給油量が確保できなくなるが、差圧によりほぼ吐出
圧力に保たれた潤滑油を軸受部に導くことができ、潤滑
油は軸受部を給油した後第１の背圧室に入り絞り通路を
介して第２の背圧室に導かれる。この際、軸受部の圧力
は密閉室内の吐出給力より若干低い圧力となるため、排
油通路に設けられた弁は閉止状態となり排油通路から吐
出圧力の冷媒ガスが軸受部及び背圧室へ流入することが
ないので安定した給油が可能となる。第２の背圧室に導
かれた潤滑油は中間孔あるいは吸入室に連通する通路を
通って圧縮室に入り、冷媒ガスと共に密閉容器内に吐出
され潤滑油部に戻る。On the other hand, during low speed operation, the amount of oil supplied cannot be secured due to the centrifugal pump action, but the lubricating oil kept at the discharge pressure due to the differential pressure can be guided to the bearing portion, and the lubricating oil supplied to the bearing portion. After that, it enters the first back pressure chamber and is guided to the second back pressure chamber through the throttle passage. At this time, the pressure in the bearing becomes slightly lower than the discharge supply force in the sealed chamber, so the valve provided in the oil drain passage is closed and refrigerant gas at the discharge pressure from the oil drain passage to the bearing and the back pressure chamber. Since there is no inflow, stable refueling is possible. The lubricating oil guided to the second back pressure chamber enters the compression chamber through the intermediate hole or a passage communicating with the suction chamber, is discharged into the closed container together with the refrigerant gas, and returns to the lubricating oil portion.

【００１３】よって、本構造により従来遠心ポンプ単独
では給油量が確保できなかった低速運転域でも運転可能
となる。Therefore, with this structure, it becomes possible to operate even in a low speed operation range where the conventional centrifugal pump alone cannot secure the amount of oil supply.

【００１４】[0014]

【発明の実施の形態】以下、本発明のスクロール圧縮機
を各図に示された実施例について詳細に説明する。BEST MODE FOR CARRYING OUT THE INVENTION The scroll compressor of the present invention will be described in detail below with reference to the embodiments shown in the drawings.

【００１５】図１は本発明の第１の実施例に係るスクロ
ール圧縮機が示されている。図２は旋回および主軸受部
の詳細構造を示す。FIG. 1 shows a scroll compressor according to a first embodiment of the present invention. FIG. 2 shows a detailed structure of the swivel and main bearing portions.

【００１６】図１で、１は固定スクロールで端板１ａと
端板１ａに直立する渦巻状のラップ１ｂを有しラップ外
周側に吸入ポート１ｃを有しラップ中央部に吐出ポート
１ｄを有している。In FIG. 1, reference numeral 1 denotes a fixed scroll having an end plate 1a and a spiral wrap 1b which stands upright on the end plate 1a, an intake port 1c on the outer peripheral side of the wrap, and a discharge port 1d at the center of the wrap. ing.

【００１７】２は旋回スクロールで、端板２ａと端板２
ａに直立する渦巻状のラップ２ｂを有し、ラップの背面
中央に旋回軸受部３０を有し、ラップ２ｂの側面に近い
位置で端板２ａを貫通する細径の中間孔２ｅが設けられ
ている。固定スクロール１と旋回スクロール２は互いに
ラップを内側として噛み合い圧縮室を形成している。Reference numeral 2 is an orbiting scroll, which includes an end plate 2a and an end plate 2
a has a spiral wrap 2b standing upright, has a slewing bearing portion 30 in the center of the back surface of the wrap, and has a small-diameter intermediate hole 2e penetrating the end plate 2a at a position close to the side surface of the wrap 2b. There is. The fixed scroll 1 and the orbiting scroll 2 mesh with each other with the wraps inside to form a compression chamber.

【００１８】３は主フレームで側面にはガス通路３ｄが
設けられ、固定スクロール１を複数のボルトで固定し、
旋回スクロール端板２ａを固定スクロール１と主フレー
ム弁座部３ａで挟持している。主フレーム３の中央部に
は主軸受部３１を備えている。また、主フレーム３に設
けられたリング溝３ｂにはシール部材４が保持されてい
る。シール部材４は旋回スクロール２の十分なめらかに
加工された鍔部２ｄに摺動自在に密着している。旋回ス
クロール２の背面の空間はシール部材４により第１の背
圧室９９と第２の背圧室９に仕切られている。第１の背
圧室９９は旋回軸受部３０および主軸受部３１に連通し
ている。第２の背圧室９は中間孔２ｅにより圧縮室に連
通している。The main frame 3 is provided with a gas passage 3d on its side surface, and the fixed scroll 1 is fixed with a plurality of bolts.
The orbiting scroll end plate 2a is sandwiched between the fixed scroll 1 and the main frame valve seat portion 3a. A main bearing portion 31 is provided at the center of the main frame 3. A seal member 4 is held in a ring groove 3b provided in the main frame 3. The seal member 4 is slidably adhered to the sufficiently smoothed flange portion 2d of the orbiting scroll 2. The space on the back surface of the orbiting scroll 2 is partitioned by the seal member 4 into a first back pressure chamber 99 and a second back pressure chamber 9. The first back pressure chamber 99 communicates with the orbiting bearing portion 30 and the main bearing portion 31. The second back pressure chamber 9 communicates with the compression chamber through the intermediate hole 2e.

【００１９】主フレーム３に第１の背圧室９９と主フレ
ーム３の下方空間とを連通させる排油孔１９が設けら
れ、排油孔１９には排油パイプ２０が取付けられてい
る。排油ポンプ２０の開口部に弁２０１が設けられてい
る。The main frame 3 is provided with an oil drain hole 19 for communicating the first back pressure chamber 99 with the space below the main frame 3, and an oil drain pipe 20 is attached to the oil drain hole 19. A valve 201 is provided at the opening of the oil drain pump 20.

【００２０】５はオルダムリングで、第２の背圧室９内
に取付けられており、固定スクロール１と旋回スクロー
ル２の自転防止部材である。オルダムリング５は直行す
る二対のキーを有し、旋回スクロールの端板２ａに設け
た一対のキー溝（図示せず）および主フレーム台座部３
ａの外側部位置に設けられた一対のキー溝３ｃに係合し
ている。An Oldham ring 5 is mounted in the second back pressure chamber 9 and serves as a rotation preventing member for the fixed scroll 1 and the orbiting scroll 2. The Oldham ring 5 has two pairs of orthogonal keys, a pair of key grooves (not shown) provided in the end plate 2a of the orbiting scroll, and the main frame pedestal portion 3.
It engages with a pair of keyways 3c provided at the outer position of a.

【００２１】６はクランク軸で電動機７を挟んで位置す
る主フレーム３に設けた主軸受部３１と副フレーム８に
設けた副軸受部３２で支持される。Reference numeral 6 is supported by a main bearing portion 31 provided on the main frame 3 and a sub bearing portion 32 provided on the sub frame 8 which are located on both sides of the electric motor 7 with the crankshaft.

【００２２】クランク軸６は内部に給油通路２３および
これに連通し回転中心に対してクランク部６ａの偏芯方
向へ偏芯して設けた給油通路２２を有し、給油通路２２
から主軸受部３１にはクランク軸径方向に分岐する給油
路２２ｂで給油し、副軸受部３２にはクランク軸径方向
に分岐する給油路２２ａで給油し、旋回軸受部には給油
路２２からクランク軸上端面の空間２ｈを利用して給油
する給油通路を形成している。The crankshaft 6 has therein an oil supply passage 23 and an oil supply passage 22 which is connected to the crankshaft 6 and is eccentrically provided in the eccentric direction of the crank portion 6a with respect to the rotation center.
To the main bearing portion 31 through the oil supply passage 22b that branches in the crankshaft radial direction, the auxiliary bearing portion 32 through the oil supply passage 22a that branches in the crankshaft radial direction, and the swivel bearing portion from the oil supply passage 22. The space 2h on the upper end surface of the crankshaft is used to form an oil supply passage for oil supply.

【００２３】電動機７は電動機ステータ７ａとクランク
軸６に固定された電動機ロータ７ｂより構成される。副
フレーム８は、径方向の位置合わせが可能となってお
り、副フレーム８に保持した副軸受部３２の軸心が主軸
受部３１の軸心に一致する位置で、副フレーム支え１０
に数本のボルトで固定されている。The electric motor 7 comprises an electric motor stator 7a and an electric motor rotor 7b fixed to the crankshaft 6. The sub-frame 8 can be aligned in the radial direction, and the sub-frame support 10 is held at a position where the axis of the sub-bearing portion 32 held by the sub-frame 8 matches the axis of the main bearing 31.
It is fixed with a few bolts.

【００２４】副軸受部３２は内面をすべり軸受面とし、
外部を球面形状とし、副フレーム８の球面形状のハウジ
ング内に微小隙間を持って嵌合された構造で、調芯機能
を有している。副軸受部３２は給油路２２ａにより給油
される。The inner surface of the sub bearing 32 is a sliding bearing surface,
It has a spherical outer shape and is fitted in the spherical housing of the sub-frame 8 with a minute gap, and has a centering function. The sub bearing portion 32 is supplied with oil by the oil supply passage 22a.

【００２５】１１は主バランスウエイトで電動機７の上
方の位置でクランク軸６に圧入固定されており、１２は
副バランスウエイトで電動機ロータ７ｂに固定されてい
る。１３は潤滑油、１４は密閉容器で密閉容器内は吐出
圧力に保持され、密閉容器胴部１４ａは主フレーム３と
電動機ステータ７ａおよび副フレーム支え１０を固定支
持する。１６は吸入口、１７は吐出口でそれぞれ密閉容
器１４を貫通している。１８はガスガイドで密閉容器１
４に取付けられている。２１は給油パイプで、クランク
軸６の下端に圧入されており、給油通路２２に連通して
いる。給油パイプ２１の下端部は潤滑油１３中に開口し
ている。Reference numeral 11 is a main balance weight, which is press-fitted and fixed to the crankshaft 6 at a position above the electric motor 7, and reference numeral 12 is an auxiliary balance weight, which is fixed to the electric motor rotor 7b. Reference numeral 13 is a lubricating oil, 14 is a closed container, and the inside of the closed container is maintained at a discharge pressure, and the closed container body 14a fixedly supports the main frame 3, the electric motor stator 7a, and the sub-frame support 10. Reference numeral 16 is a suction port, and 17 is a discharge port, which penetrate the sealed container 14, respectively. 18 is a gas guide and a closed container 1
It is attached to 4. Reference numeral 21 denotes an oil supply pipe, which is press-fitted into the lower end of the crankshaft 6 and communicates with the oil supply passage 22. The lower end of the oil supply pipe 21 opens into the lubricating oil 13.

【００２６】クランク軸６のクランク部６ａは旋回スク
ロール２の旋回軸受部３０に連結している。旋回軸受部
３０は内面をすべり軸受面とし、軸受面に軸受面を貫通
するスパイラル状の給油溝３０ａが設けられている。ス
パイラル溝３０ａはクランク軸６の回転に伴い給油を促
進する方向に粘性ポンプ作用が働くように設けられてい
る。The crank portion 6a of the crankshaft 6 is connected to the orbiting bearing portion 30 of the orbiting scroll 2. The orbiting bearing portion 30 has an inner surface as a slide bearing surface, and a spiral oil supply groove 30a penetrating the bearing surface is provided on the bearing surface. The spiral groove 30a is provided so that a viscous pump action works in a direction of promoting oil supply as the crankshaft 6 rotates.

【００２７】主軸受部３１は内面をすべり軸受面とし、
軸受面にクランク軸の給油路２２ｂに相対する位置に円
周溝３１ｂが設けられ、円周溝３１ｂと軸受端面を貫通
するスパイラル状の給油溝３１ａが設けられている。ス
パイラル溝３１ａはクランク軸６の回転に伴い給油を促
進する方向に粘性ポンプ作用が働くように設けられてい
る。The inner surface of the main bearing portion 31 is a sliding bearing surface,
A circumferential groove 31b is provided on the bearing surface at a position facing the oil feeding passage 22b of the crankshaft, and a spiral oil feeding groove 31a penetrating the circumferential groove 31b and the bearing end surface is provided. The spiral groove 31a is provided so that a viscous pump action works in a direction of promoting oil supply as the crankshaft 6 rotates.

【００２８】また、クランク軸６はスラスト受け部６ｂ
を介して主軸受部３１の上端側に設けられたスラスト軸
受３４により支持される。スラスト軸受３４の軸受面に
は主軸受部の給油溝３１ａに連通する径方向の給油路３
４ａが設けられている。旋回軸受の給油溝３０ａ，主軸
受部の給油溝３１ａは第１の背圧室９９に連通してい
る。The crankshaft 6 has a thrust receiving portion 6b.
It is supported by a thrust bearing 34 provided on the upper end side of the main bearing portion 31 via. On the bearing surface of the thrust bearing 34, the radial oil supply passage 3 communicating with the oil supply groove 31a of the main bearing portion is formed.
4a is provided. The oil supply groove 30a of the slewing bearing and the oil supply groove 31a of the main bearing portion communicate with the first back pressure chamber 99.

【００２９】図３にシール部材を示す。シール部材４は
リングの一部をカットしたＣ型の形状で、カット部４ａ
は微小隙間となるように設定されており、絞り通路とし
て機能する。図４に弁２０１の斜視図を示す。弁２０１
は弁部２０１ａ，弁ストッパ２０１ｃ、および弁部２０
１ａと弁ストッパ２０１ｃを連結する連結棒２０１ｂに
より構成されている。図５および図６に弁２０１周りの
断面図を示す。排油パイプ２０は弁側の開口部を絞り、
段付部２０ａを構成することにより、弁２０１を排油パ
イプ２０内に保持している。図５は弁２０１が解放状態
の場合を示している。排油パイプ２０内の圧力が外の圧
力（密閉容器１４内の圧力）より高い場合には差圧によ
り弁部２０１ａが排油パイプ２０から離れ解放状態とな
る。このとき、弁ストッパ２０１ｃが排油パイプ２０の
段付部２０ａに当り弁２０１が止まる。図６は弁２０１
が閉止状態の場合を示している。排油パイプ２０内の圧
力が外の圧力（密閉容器１４内の圧力）より低い場合に
は差圧により弁部２０１ａが排油パイプ２０に密着し閉
止状態となる。FIG. 3 shows the seal member. The seal member 4 has a C-shape with a part of the ring cut, and has a cut portion 4a.
Is set to be a minute gap and functions as a throttle passage. FIG. 4 shows a perspective view of the valve 201. Valve 201
Is the valve portion 201a, the valve stopper 201c, and the valve portion 20.
It is configured by a connecting rod 201b that connects 1a and the valve stopper 201c. 5 and 6 are cross-sectional views around the valve 201. The oil drain pipe 20 restricts the opening on the valve side,
The valve 201 is held in the oil drain pipe 20 by configuring the stepped portion 20a. FIG. 5 shows the case where the valve 201 is in the open state. When the pressure inside the oil drain pipe 20 is higher than the pressure outside (the pressure inside the closed container 14), the valve portion 201a is separated from the oil drain pipe 20 due to the differential pressure and is in a released state. At this time, the valve stopper 201c hits the stepped portion 20a of the oil drain pipe 20 and the valve 201 stops. FIG. 6 shows a valve 201
Shows the case where is closed. When the pressure in the oil drain pipe 20 is lower than the external pressure (the pressure in the closed container 14), the valve portion 201a is brought into close contact with the oil drain pipe 20 due to the differential pressure, and the valve is closed.

【００３０】次に、本発明の実施例の動作を説明する。Next, the operation of the embodiment of the present invention will be described.

【００３１】電動機７に外部より電気が供給されると、
電動機ロータ７ｂが回転し、これに伴ってクランク軸６
が回転する。結果、旋回スクロール２は、オリダムリン
グ５の介在により旋回運動して、冷媒ガスが吸入口１６
から吸入ポート１ｃを通り流入し、圧縮室に取込まれ、
旋回スクロール２の運動に伴って冷媒ガスは圧縮され、
高圧になった冷媒ガスは吐出ポート１ｄより固定スクロ
ール１上部空間に吐出される。圧縮動作中、適当に昇圧
された冷媒ガスは中間孔２ｅを介して第２の背圧室９に
充満する。旋回スクロール端板２ａは主フレーム３の台
座部３ａと固定スクロール１に挟持されているため、旋
回スクロール２は起動開始時に傾いたりしないで、固定
スクロール１に押付けられる。When electric power is supplied to the electric motor 7 from the outside,
The electric motor rotor 7b rotates, and the crankshaft 6
Rotates. As a result, the orbiting scroll 2 orbits due to the Oridham ring 5, and the refrigerant gas is sucked into the inlet 16
Flows in through the suction port 1c and is taken into the compression chamber,
The refrigerant gas is compressed as the orbiting scroll 2 moves,
The high-pressure refrigerant gas is discharged from the discharge port 1d into the space above the fixed scroll 1. During the compression operation, the appropriately pressurized refrigerant gas fills the second back pressure chamber 9 through the intermediate hole 2e. Since the orbiting scroll end plate 2a is sandwiched between the pedestal portion 3a of the main frame 3 and the fixed scroll 1, the orbiting scroll 2 is pressed against the fixed scroll 1 without tilting at the start of activation.

【００３２】運転の経過により密閉容器１４内の圧力
（吐出圧力）は上昇し、シール部材４の内側の第１の背
圧室９９は吐出圧力に保持される。第１の背圧室９９の
吐出圧力と第２の背圧室９内圧力の合力が旋回スクロー
ル２を固定スクロール１に押付けるスラスト力として作
用する。The pressure (discharge pressure) in the closed container 14 rises with the progress of the operation, and the first back pressure chamber 99 inside the seal member 4 is maintained at the discharge pressure. The resultant force of the discharge pressure of the first back pressure chamber 99 and the pressure inside the second back pressure chamber 9 acts as a thrust force for pressing the orbiting scroll 2 against the fixed scroll 1.

【００３３】旋回スクロール２に対するスラスト力が、
圧縮室内のガス力によって生じる全スラスト力の大きさ
よりも上回るため、旋回スクロール２は固定スクロール
１側に押付けられ安定した圧縮動作が行われる。The thrust force on the orbiting scroll 2 is
Since the total thrust force generated by the gas force in the compression chamber exceeds the total thrust force, the orbiting scroll 2 is pressed against the fixed scroll 1 side and a stable compression operation is performed.

【００３４】また、吐出ポート１ｄから固定スクロール
１の上部空間に吐出された高圧ガスは、主フレーム３の
側面のガス通路３ｄを通り、電動機７上部空間に流入
し、その一部はガスガイド１８に導かれ、電動機７側面
に設けた通路から電動機７下部空間に導かれ、再び電動
機７上部空間に流入し、ここで、冷媒ガスは電動機７を
冷却すると共に、冷媒ガス中の潤滑油は分離されて冷媒
ガスは吐出口１７から圧縮機外へ流出する。一部の潤滑
油はいわゆる油上がりとなって冷媒ガスと共に機外に流
出するが、再び冷媒ガスとともにスクロール圧縮機の吸
入口１６に戻る。一方、分離された潤滑油は重力によっ
て下方に流れ落ち密閉容器下部の潤滑油部１３に到達す
る。The high-pressure gas discharged from the discharge port 1d into the upper space of the fixed scroll 1 flows into the upper space of the electric motor 7 through the gas passage 3d on the side surface of the main frame 3, and a part of the gas guide 18 flows. Is guided to the lower space of the electric motor 7 from a passage provided on the side surface of the electric motor 7 and then flows into the upper space of the electric motor 7 again, where the refrigerant gas cools the electric motor 7 and the lubricating oil in the refrigerant gas is separated. The refrigerant gas is discharged from the discharge port 17 to the outside of the compressor. A part of the lubricating oil becomes so-called oil rise and flows out of the machine together with the refrigerant gas, but returns to the suction port 16 of the scroll compressor together with the refrigerant gas again. On the other hand, the separated lubricating oil flows downward due to gravity and reaches the lubricating oil portion 13 below the closed container.

【００３５】クランク軸６が回転すると、偏芯して設け
られた給油通路２２により遠心ポンプ作用が働くため、
潤滑油は潤滑油部１３より給油パイプ２１および給油通
路２３を通り給油通路２２を上昇する。上昇した潤滑油
はクランク軸の径方向に分岐する給油路２２ｂ及びクラ
ンク軸上端の空間２ｈを通り軸受部に到達する。When the crankshaft 6 rotates, the eccentric oil supply passage 22 acts as a centrifugal pump,
The lubricating oil passes from the lubricating oil portion 13 through the oil supply pipe 21 and the oil supply passage 23 and rises in the oil supply passage 22. The elevated lubricating oil reaches the bearing portion through the oil supply passage 22b branched in the radial direction of the crankshaft and the space 2h at the upper end of the crankshaft.

【００３６】主軸受部３１には給油路２２ｂから給油路
２２ｂに相対する位置に設けられた円周溝３１ｂに給油
され、円周溝３１ｂからスパイラル状の給油溝３１ａを
介して潤滑される。スパイラル溝３１ａはランク軸６の
回転に伴い給油を促進する方向に粘性ポンプ作用が働く
ように設けられているため給油能力を軸受面内で補うこ
とができる。The main bearing portion 31 is supplied with oil from the oil supply passage 22b to a circumferential groove 31b provided at a position facing the oil supply passage 22b, and is lubricated from the circumferential groove 31b through a spiral oil supply groove 31a. Since the spiral groove 31a is provided so that the viscous pumping action works in the direction of promoting the oil supply as the rank shaft 6 rotates, the oil supply capacity can be supplemented within the bearing surface.

【００３７】また、クランク軸６を支持するスラスト軸
受３４は主軸受部の給油溝３１ａに連通する径方向の給
油路３４ａで主軸受部３１を給油した潤滑油で給油され
る。主軸受部を給油した潤滑油は第１の背圧室９９に到
達する。The thrust bearing 34, which supports the crankshaft 6, is lubricated with the lubricating oil that has lubricated the main bearing portion 31 in the radial oil passage 34a that communicates with the oil groove 31a of the main bearing portion. The lubricating oil that has supplied the main bearing reaches the first back pressure chamber 99.

【００３８】副軸受部３２は給油路２２ａにより給油さ
れ、潤滑油は潤滑油部１３に循環する。The sub bearing portion 32 is supplied with oil through the oil supply passage 22a, and the lubricating oil circulates in the lubricating oil portion 13.

【００３９】旋回軸受部３０には差圧給油路からクラン
ク軸上端の空間２ｈよりスパイラル状の給油溝３０ａを
介して潤滑される。スパイラル溝３１ａはクランク軸６
の回転に伴い給油を促進する方向に粘性ポンプ作用が働
くように設けられているため給油能力を軸受面内で補う
ことができる。旋回軸受部３０を給油した潤滑油は第１
の背圧室９９に到達する。第１の背圧室９９に到達した
旋回軸受３０，主軸受部３１を給油した潤滑油は主フレ
ーム３に設けた排油孔１９から排油パイプ２０に導かれ
る。ここで潤滑油の油圧が給油通路２２内で受けた遠心
ポンプ作用により、吐出圧力よりも上昇しているため、
排油パイプ２０の開口部に設けられた弁２０１は油圧と
吐出圧力の差圧で解放状態となり、潤滑油は密閉容器１
４内に排出され、密閉容器１４内の内壁面にそって重力
により落下する。The slewing bearing portion 30 is lubricated from the differential pressure oil supply passage through the space 2h at the upper end of the crankshaft through a spiral oil supply groove 30a. Spiral groove 31a is crankshaft 6
Since the viscous pump action is provided in the direction of promoting the oil supply with the rotation of, the oil supply capacity can be supplemented within the bearing surface. The lubricating oil that has supplied the slewing bearing portion 30 is the first
To the back pressure chamber 99. Lubricating oil that has reached the first back pressure chamber 99 and supplied to the orbiting bearing 30 and the main bearing portion 31 is guided to the oil drain pipe 20 through the oil drain hole 19 provided in the main frame 3. Here, since the oil pressure of the lubricating oil is higher than the discharge pressure due to the centrifugal pump action received in the oil supply passage 22,
The valve 201 provided at the opening of the oil drain pipe 20 is released due to the pressure difference between the hydraulic pressure and the discharge pressure, and the lubricating oil is sealed in the closed container 1.
4 and is dropped by gravity along the inner wall surface of the closed container 14.

【００４０】このように主軸受部３１，旋回軸受部３０
を給油した潤滑油は冷媒ガス通路と別の経路で密閉容器
１４下部へ落下するため、冷媒ガスに混合し機外に流出
することなく、密閉容器１４下部に潤滑油部１３に循環
する。Thus, the main bearing portion 31 and the slewing bearing portion 30 are
Since the lubricating oil that has been supplied drops to the lower portion of the closed container 14 through a route different from the refrigerant gas passage, it is circulated to the lubricating oil portion 13 below the closed container 14 without being mixed with the refrigerant gas and flowing out of the machine.

【００４１】一方、シール部材４のカット部４ａの微小
隙間は絞り通路として機能し、絞り通路の面積はクラン
ク軸６内の給油通路２２に対して十分通路面積を絞られ
ているので、クランク軸６内の給油通路２２内では潤滑
油の油圧を低下させずに第１の背圧室９９と第２の背圧
室９との差圧を利用して第２の背圧室９に潤滑油を導く
ことができる。このため、軸受部に給油される潤滑油量
は、遠心ポンプ作用により送られる潤滑油と、差圧によ
り導かれる潤滑油の合計となる。したがって、低速運転
域で遠心ポンプ作用のみでは軸受部に潤滑油が到達でき
ない場合にも差圧により潤滑油が導かれるため運転が可
能となる。また、低速運転域では遠心ポンプ作用が十分
でないため、軸受部に給油された潤滑油の油圧は吐出圧
力より低い圧力となる場合があるが、排油パイプ２０の
開口部に設けられた弁２０１が油圧と吐出圧力の差圧で
閉止することにより、密閉容器１４内の吐出圧力の冷媒
ガスが排油パイプ２０から第１の背圧室９９に流入する
のを防止し、安定した給油を確保することができる。第
２の背圧室９に導かれた潤滑油は、第２の背圧室９に配
置されたオルダムリング５を潤滑する。オルダムリング
５を潤滑した後の潤滑油は中間孔２ｅを通って圧縮室に
入り、冷媒ガスとともに吐出ポート１ｄから吐出される
ため、従来の絞り通路による差圧給油のスクロール圧縮
機と同様、入力増加を招くとともに冷媒ガスと混合して
機外に流出しやすくなるが、本構造では遠心ポンプ作用
と差圧の両方を利用して給油するため、差圧により導く
潤滑油量が低速運転域の必要油量以上にならないように
絞り通路の面積を設定することにより、圧縮室に入る潤
滑油量を抑制できるので従来に比べ上記の問題点を大幅
に改善できる。On the other hand, the minute gap of the cut portion 4a of the seal member 4 functions as a throttle passage, and the area of the throttle passage is sufficiently narrowed with respect to the oil supply passage 22 in the crankshaft 6, so that the crankshaft In the oil supply passage 22 in 6, the oil pressure of the lubricating oil is not reduced and the differential pressure between the first back pressure chamber 99 and the second back pressure chamber 9 is utilized to make the lubricating oil flow to the second back pressure chamber 9. Can be guided. Therefore, the amount of lubricating oil supplied to the bearing portion is the total of the lubricating oil sent by the centrifugal pump action and the lubricating oil introduced by the differential pressure. Therefore, even if the lubricating oil cannot reach the bearing portion only by the centrifugal pump action in the low speed operation range, the lubricating oil is guided by the differential pressure, and thus the operation can be performed. Further, since the centrifugal pump action is not sufficient in the low speed operation range, the oil pressure of the lubricating oil supplied to the bearing portion may be lower than the discharge pressure, but the valve 201 provided at the opening of the oil drain pipe 20 may be used. Is closed by the differential pressure between the hydraulic pressure and the discharge pressure, so that the refrigerant gas at the discharge pressure in the closed container 14 is prevented from flowing into the first back pressure chamber 99 from the oil discharge pipe 20, and a stable oil supply is ensured. can do. The lubricating oil guided to the second back pressure chamber 9 lubricates the Oldham ring 5 arranged in the second back pressure chamber 9. Since the lubricating oil after lubricating the Oldham ring 5 enters the compression chamber through the intermediate hole 2e and is discharged from the discharge port 1d together with the refrigerant gas, it is input as in the conventional scroll compressor for differential pressure oil supply by the throttle passage. Although it causes an increase and it easily mixes with the refrigerant gas and flows out of the machine, this structure uses both the centrifugal pump action and the differential pressure to supply oil, so the amount of lubricating oil introduced by the differential pressure is in the low-speed operating range. By setting the area of the throttle passage so as not to exceed the required amount of oil, the amount of lubricating oil entering the compression chamber can be suppressed, so that the above-mentioned problems can be greatly improved compared to the conventional case.

【００４２】図７は絞り通路の第２の実施例で旋回スク
ロール２の鍔部２ｄの斜視図である。鍔部２ｄのシール
部材４との接触面にＶ溝２ｊを設けた例であり、カット
部４ａによる絞り通路と同等の働きをする。また、構造
ではシール部材４はカットなしのリング形状でもよい。FIG. 7 is a perspective view of the flange portion 2d of the orbiting scroll 2 in the second embodiment of the throttle passage. This is an example in which the V groove 2j is provided on the contact surface of the flange portion 2d with the seal member 4, and the same function as the throttle passage by the cut portion 4a is obtained. Further, in the structure, the seal member 4 may have a ring shape without cut.

【００４３】図８は絞り通路の第３の実施例でシール部
材４周りの詳細断面図を示す。図９は同実施例のフレー
ム３のリング溝３ｂの拡大図である。シール部材４を板
ばね２４により押し上げ鍔部２ｄに密着させる構造の場
合にリング溝３ｂの外側内壁面部に微小切欠き溝３ｆを
設け絞り通路を構成した例であり、カット部４ａによる
絞り通路と同等の働きをする。また、構造ではシール部
材４はカットなしのリング形状でもよい。FIG. 8 is a detailed sectional view around the seal member 4 in the third embodiment of the throttle passage. FIG. 9 is an enlarged view of the ring groove 3b of the frame 3 of the same embodiment. In the case of the structure in which the seal member 4 is pushed up by the leaf spring 24 and brought into close contact with the flange portion 2d, this is an example in which a minute cutout groove 3f is provided on the outer inner wall surface portion of the ring groove 3b to form a throttle passage. Do the same. Further, in the structure, the seal member 4 may have a ring shape without cut.

【００４４】図１０は第２の背圧室９を吸入圧力とした
実施例である。第２の背圧室９は連通孔１ｆにより吸入
室と連通しており、吸入圧力となる。旋回スクロール２
は台座３ａ上面をスラスト面とし固定スクロール１に対
して離脱しないように保持されている。シール部材４に
は、図３に示したカット部４ａが設けられ絞り通路を構
成している。第１の背圧室９９は実施例と同様軸受部と
連通しており吐出圧力とほぼ同等の圧力に保持される。
第１の背圧室９９と第２の背圧室９との差圧により潤滑
油は軸受部を給油しカット部４ａの絞り通路を介して第
２の背圧室９へ導かれる。第２の背圧室９へ導かれた潤
滑油はカルダムリング５の摺動部を潤滑した後、連通孔
１ｆを介して吸入室に流入し冷媒ガスとともに圧縮室を
経て機内に吐出される。遠心ポンプ作用による給油につ
いては実施例と同様である。FIG. 10 shows an embodiment in which the second back pressure chamber 9 has a suction pressure. The second back pressure chamber 9 communicates with the suction chamber through the communication hole 1f, and has a suction pressure. Orbiting scroll 2
The upper surface of the pedestal 3a serves as a thrust surface and is held so as not to separate from the fixed scroll 1. The seal member 4 is provided with the cut portion 4a shown in FIG. 3 to form a throttle passage. The first back pressure chamber 99 communicates with the bearing portion as in the embodiment, and is maintained at a pressure substantially equal to the discharge pressure.
Due to the pressure difference between the first back pressure chamber 99 and the second back pressure chamber 9, the lubricating oil supplies the bearing portion and is guided to the second back pressure chamber 9 through the throttle passage of the cut portion 4a. The lubricating oil guided to the second back pressure chamber 9 lubricates the sliding portion of the Cardham ring 5, then flows into the suction chamber through the communication hole 1f, and is discharged into the machine through the compression chamber together with the refrigerant gas. . The refueling by the centrifugal pump action is the same as in the embodiment.

【００４５】[0045]

【発明の効果】本発明によれば、遠心ポンプ作用と差圧
の両方を利用した給油経路が構成でき、従来の遠心ポン
プ給油方法単独ではポンプ能力が低下し運転できなかっ
た低速運転でも各摺動面への安定した給油が可能とな
り、可変速スクロール圧縮機の低速運転域を拡大するこ
とができる。According to the present invention, an oil supply path utilizing both centrifugal pump action and differential pressure can be constructed, and the conventional centrifugal pump oil supply method alone cannot reduce the pumping capacity and cannot operate even at low speeds. Stable oil supply to the moving surface is possible, and the low speed operation range of the variable speed scroll compressor can be expanded.

【図面の簡単な説明】[Brief description of the drawings]

【図１】本発明の実施例で縦型のスクロール圧縮機の断
面図。FIG. 1 is a sectional view of a vertical scroll compressor according to an embodiment of the present invention.

【図２】図１の部分断面図。FIG. 2 is a partial sectional view of FIG.

【図３】シール部材の平面図。FIG. 3 is a plan view of a seal member.

【図４】弁の斜視図。FIG. 4 is a perspective view of a valve.

【図５】弁周りの解放時の断面図。FIG. 5 is a cross-sectional view around the valve when it is released.

【図６】弁周りの閉止時の断面図。FIG. 6 is a sectional view around the valve when the valve is closed.

【図７】鍔部の斜視図。FIG. 7 is a perspective view of a collar portion.

【図８】シール部材周りの断面図。FIG. 8 is a cross-sectional view around a seal member.

【図９】リング溝の拡大図。FIG. 9 is an enlarged view of a ring groove.

【図１０】第２の背圧室を吸入圧力とした実施例の部分
断面図。FIG. 10 is a partial cross-sectional view of an embodiment in which a second back pressure chamber has a suction pressure.

【図１１】従来の圧縮機の断面図。FIG. 11 is a sectional view of a conventional compressor.

【符号の説明】[Explanation of symbols]

２…旋回スクロール、４…シール部材、９，９９…背圧
室、２０…排油パイプ、２０１…弁。2 ... Orbiting scroll, 4 ... Seal member, 9, 99 ... Back pressure chamber, 20 ... Oil drain pipe, 201 ... Valve.

───────────────────────────────────────────────────── フロントページの続き (72)発明者 岡田 光弘 静岡県清水市村松390番地 株式会社日立 製作所空調システム事業部内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Mitsuhiro Okada 390 Muramatsu, Shimizu City, Shizuoka Prefecture Hitachi Ltd. Air Conditioning Systems Division

Claims (1)

【特許請求の範囲】[Claims] 【請求項１】密閉容器内に端板と、前記端板に直立する
渦巻状のラップとを有した固定スクロールおよび旋回ス
クロールを互いにラップを内側として噛み合い圧縮室を
形成し、前記旋回スクロールを旋回運動させるクランク
軸と、前記クランク軸を支持する主フレームとを含む圧
縮機構部と、前記圧縮機構部を駆動する電動機と、潤滑
油部とを備え、前記密閉容器内を吐出口に連通して吐出
圧力に維持し、前記旋回スクロールの背面に複数の背圧
室を形成し、少なくとも一つのシール部材を前記背圧室
間に設け、軸受部と連通し吐出圧力とほぼ等しい圧力を
維持する第１の背圧室と吐出圧力より低い圧力を維持す
る第２の背圧室を構成したスクロール圧縮機において、
前記軸受部に給油した潤滑油を前記潤滑油部へ導く一方
向へのみ流れる排油通路を設けたことを特徴とするスク
ロール圧縮機。1. A fixed scroll and an orbiting scroll each having an end plate and a spiral wrap standing upright on the end plate in an airtight container are meshed with each other with the wraps inside to form a compression chamber, and the orbiting scroll is orbited. A compression mechanism section including a crankshaft to be moved and a main frame supporting the crankshaft, an electric motor driving the compression mechanism section, and a lubricating oil section are provided, and the inside of the closed container is communicated with a discharge port. A discharge pressure is maintained, a plurality of back pressure chambers are formed on the back surface of the orbiting scroll, and at least one seal member is provided between the back pressure chambers so as to communicate with the bearing portion and maintain a pressure substantially equal to the discharge pressure. In a scroll compressor having a first back pressure chamber and a second back pressure chamber that maintains a pressure lower than the discharge pressure,
A scroll compressor, characterized in that an exhaust oil passage is provided to flow the lubricating oil supplied to the bearing portion to the lubricating oil portion and flow only in one direction.