JPH08284853A - Scroll compressor - Google Patents
Scroll compressorInfo
- Publication number
- JPH08284853A JPH08284853A JP8667295A JP8667295A JPH08284853A JP H08284853 A JPH08284853 A JP H08284853A JP 8667295 A JP8667295 A JP 8667295A JP 8667295 A JP8667295 A JP 8667295A JP H08284853 A JPH08284853 A JP H08284853A
- Authority
- JP
- Japan
- Prior art keywords
- end plate
- orbiting scroll
- oldham
- scroll
- scroll member
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
- F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
- F01C17/066—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements with an intermediate piece sliding along perpendicular axes, e.g. Oldham coupling
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、冷凍空調用・冷蔵庫用
等の冷媒用圧縮機として用いられる密閉形スクロール圧
縮機に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hermetic scroll compressor used as a refrigerant compressor for refrigeration and air conditioning, refrigerators and the like.
【０００２】[0002]
【従来の技術】従来の技術のスクロール圧縮機は、特開
昭59−141783号や特開昭62−75094 号公報に開示されて
いるように、スクロール圧縮機構部で圧縮された冷媒ガ
スは、上部の吐出室から連通路を介して電動機室に至
る。次いで冷媒ガスは、電動機の周囲を通って、圧縮機
の吐出管から外部に流出する。2. Description of the Related Art As disclosed in JP-A-59-141783 and JP-A-62-75094, a scroll compressor of the prior art discloses a refrigerant gas compressed by a scroll compression mechanism, From the upper discharge chamber to the electric motor chamber via the communication passage. Then, the refrigerant gas flows around the electric motor and flows out from the discharge pipe of the compressor to the outside.
【０００３】[0003]
【発明が解決しようとする課題】従来技術の引用例で
は、旋回スクロールの鏡板外周部の側部空間には一種の
密閉空間となっているため、その空間は軸受部から排出
された潤滑油が溜められやすい構造となっている。この
ため、旋回スクロールの旋回運動によってその鏡板外周
部の側部空間内での油撹拌損失が生じることになる。ま
た、自転防止機構であるオルダム機構部の摺動部では、
圧縮機停止時には油がきれて再起動時における油量不足
が生じる。この油量不足によるオルダム機構部の摺動部
の潤滑性能が損なわれるとともにかじり等の信頼性が低
下する課題がある。また、回転数が一万rpm などと圧縮
機の高速化を達成しようとすると油撹拌損失が約回転数
の三乗ないし四乗に比例して大きくなり、圧縮機の性能
が顕著に低下するという問題がある。In the cited reference of the prior art, since the side space on the outer peripheral portion of the end plate of the orbiting scroll is a kind of closed space, the space is filled with the lubricating oil discharged from the bearing portion. It has a structure that can be easily stored. Therefore, the orbiting motion of the orbiting scroll causes an oil agitation loss in the side space of the outer peripheral portion of the end plate. In addition, at the sliding part of the Oldham mechanism, which is a rotation prevention mechanism,
When the compressor is stopped, the oil runs out, causing a shortage of oil when restarting. Due to this insufficient amount of oil, there are problems that the lubrication performance of the sliding part of the Oldham mechanism part is impaired and the reliability such as galling decreases. Also, when trying to achieve a high speed compressor with a rotation speed of 10,000 rpm, etc., the oil agitation loss increases in proportion to the third or fourth power of the rotation speed, which significantly reduces the performance of the compressor. There's a problem.
【０００４】また、従来構造では高速化とともに、旋回
キー部に作用する自転力が遠心力分が増大して、旋回キ
ー部に作用する面圧ＰＶ及びＰＶ値（Ｖ：摩擦速度）が
高くなって、旋回キー摺動部の摩耗が促進する課題も派
生する。このように、本発明の目的は圧縮機の性能低下
と信頼性低下を解決することにある。Further, in the conventional structure, as the speed is increased, the rotation force acting on the turning key portion is increased by the centrifugal force, and the surface pressure PV and PV value (V: friction speed) acting on the turning key portion are increased. As a result, there arises a problem that wear of the turning key sliding portion is accelerated. As described above, an object of the present invention is to solve the performance deterioration and reliability deterioration of the compressor.
【０００５】[0005]
【課題を解決するための手段】本発明では、旋回スクロ
ール鏡板外周部の背面部に背圧室と旋回スクロール鏡板
外周部の側部空間とをシールするシール手段を備え、前
記側部空間と吸入室とを連通するためスラスト軸受面と
なる固定スクロールの鏡板外周面に放射状溝部を備える
構成とする。また、中央部の主軸を支持するフレームの
上方部に旋回スクロールの鏡板外周部の背面部を支える
鏡板支持座を形成し、旋回スクロールの自転防止部材と
してオルダムリング部およびオルダムキー部よりなるオ
ルダム機構を旋回スクロールとフレームとの間に配置
し、オルダムリング本体部が軸方向に対向するフレーム
台座面に対して前記フレーム側オルダムキー溝部の内周
端部に微小な突起部を備え、前記鏡板支持座の内周部と
オルダムキー溝部の内周端部との間に油溜め部を構成し
たことを特徴としている。さらに、前記オルダム機構
で、旋回鏡板背面部にキー溝部と摺動接触するオルダム
キー部の外法寸法をオルダムリング本体部のリング外径
より大きくなるように凸部を備え、前記旋回側オルダム
キー凸部の外径がフレーム側キー溝部と摺動接触するオ
ルダムキー部の外法寸法より大きく設定したことを特徴
としている。In the present invention, a sealing means for sealing the back pressure chamber and the side space of the outer peripheral portion of the orbiting scroll end plate is provided on the back surface of the outer peripheral portion of the orbiting scroll end plate, and the side space and the suction are provided. A radial groove is provided on the outer peripheral surface of the end plate of the fixed scroll which serves as a thrust bearing surface for communicating with the chamber. In addition, an end plate support seat that supports the rear surface of the outer peripheral part of the orbiting scroll is formed in the upper part of the frame that supports the main shaft of the central part, and an Oldham mechanism consisting of an Oldham ring part and an Oldham key part is used as a rotation preventing member of the orbiting scroll. Arranged between the orbiting scroll and the frame, the Oldham ring main body is provided with a minute projection at the inner peripheral end of the frame-side Oldham key groove portion with respect to the frame pedestal surface facing in the axial direction. It is characterized in that an oil sump portion is formed between the inner peripheral portion and the inner peripheral end portion of the Oldham key groove portion. Furthermore, in the Oldham mechanism, a convex portion is provided on the back end of the swivel end plate so that the outer dimension of the Oldham key portion that is in sliding contact with the key groove portion is larger than the ring outer diameter of the Oldham ring body portion. The outer diameter of is set to be larger than the outer dimension of the Oldham key portion that makes sliding contact with the key groove portion on the frame side.
【０００６】[0006]
【作用】本発明の作用を図１から図１５をもとにして説
明する。図１で、旋回スクロール６の鏡板外周部６ａの
背面部に背圧室３６と旋回スクロール鏡板外周部の側部
空間１１ｆとをシールするシール手段３４を備えている
ため、軸受隙間から流出した背圧室３６内部の油が、側
部空間１１ｆへの流入を阻止するため、側部空間１１ｆ
の油溜り現象が回避される。また、仮に油が微量混入さ
れたとしても、図４に示すように、この側部空間１１ｆ
と吸入室とが固定スクロール５の鏡板外周面５ｋに設け
た放射状溝部５ｒによって吸入室５ｆ側に、旋回スクロ
ールの偏心した旋回運動によりスムースに油が排出・移
動することになる。また、この排油がスラスト軸受面と
なっている固定スクロール５の鏡板外周面５ｋの潤滑に
供される。このため、摺動面での油潤滑が確実に行わ
れ、この部分での摺動性能が改善されひいては摺動損失
が低減する。この様な構造とすることにより、スラスト
摺動部での潤滑性能を向上させ、スクロール部材の耐摩
耗性も改善できる。また、図６に示すように、旋回スク
ロール６の鏡板背面のシール手段３４の内側領域には吐
出圧力Ｐｄと吸入圧力Ｐｓとの中間圧力Ｐｍが作用し、
シール手段３４の外側領域は吸入圧力Ｐｓの雰囲気にし
ている。従来機に対して、側部空間１１ｆ（フレーム
室）から吸入室５ｆへの高温の油もれを大きく防止でき
るので、吸入ガスの内部加熱量を軽減できる。このた
め、高速回転時でも、油撹拌損失が低減し、圧縮機の動
力が低下し、吸入ガスの内部加熱量低下による体積効率
の向上によって、全断熱効率の向上が大幅にはかれる。
また、この効果と作用は、軸受油量が増加して吸入ガス
の内部加熱量が増加する高圧力比での運転条件で顕著と
なる。The operation of the present invention will be described with reference to FIGS. In FIG. 1, since the back pressure chamber 36 and the side space 11f on the outer peripheral portion of the orbiting scroll end plate are provided with a sealing means 34 on the back surface of the outer peripheral portion 6a of the orbiting scroll 6, the back flow out of the bearing gap is provided. Since the oil inside the pressure chamber 36 blocks the inflow into the side space 11f, the side space 11f
The oil puddle phenomenon is avoided. Moreover, even if a small amount of oil is mixed, as shown in FIG.
The oil is smoothly discharged and moved to the suction chamber 5f side by the radial groove 5r provided on the outer peripheral surface 5k of the end plate of the fixed scroll 5 and the suction chamber due to the eccentric orbiting motion of the orbiting scroll. Further, this drained oil is used to lubricate the outer peripheral surface 5k of the end plate of the fixed scroll 5 serving as the thrust bearing surface. Therefore, oil lubrication on the sliding surface is surely performed, sliding performance in this portion is improved, and sliding loss is reduced. With such a structure, the lubrication performance in the thrust sliding portion can be improved and the wear resistance of the scroll member can also be improved. Further, as shown in FIG. 6, an intermediate pressure Pm between the discharge pressure Pd and the suction pressure Ps acts on the inner area of the sealing means 34 on the rear surface of the end plate of the orbiting scroll 6,
The outside region of the sealing means 34 is set to the atmosphere of the suction pressure Ps. Compared with the conventional machine, high temperature oil leakage from the side space 11f (frame chamber) to the suction chamber 5f can be largely prevented, so that the internal heating amount of the suction gas can be reduced. Therefore, even at high speed rotation, the oil agitation loss is reduced, the power of the compressor is reduced, and the volumetric efficiency is improved by reducing the internal heating amount of the suction gas, so that the total adiabatic efficiency is significantly improved.
Further, this effect and action become remarkable under the operating condition at a high pressure ratio in which the amount of bearing oil increases and the amount of internal heating of the intake gas increases.
【０００７】次に、図１０から図１２で、中央部の主軸
１４を支持するフレーム１１の上方部に旋回スクロール
６の鏡板外周部の背面部を支える鏡板支持座１１ｅとフ
レーム側オルダムキー溝部５２ｍの内周端部５８の微小
な突起部５１との間に油溜め部５７を構成することにな
る。このため、圧縮機が停止されてもその部分には油が
残っており、特にオルダムキー溝部５２ｍには常に油が
有る。そして、圧縮機の再起動時では、従来機のうおう
な油量不足が生じることがなくなる。また、油量不足に
よるオルダム機構部の摺動部の潤滑性能が損なわれるこ
とも解消され、そのオルダム機構部の信頼性が向上でき
る。さらに、図１３で、オルダム機構で、旋回鏡板背面
部のキー溝部と摺動接触するオルダムキー部３ａのキー
面積をフレーム側より大きく設定することで、キー部に
作用する面圧をフレーム側より低減できることになる。
また、そのキー部３ａの外法寸法Ｄor1 をオルダムリン
グ本体部３ｍのリング外径Ｄor2 より大きくしているの
で、旋回側のキー部３ａに作用する荷重をフレーム１１
側のキー部３ｂに作用する荷重より軽減できることにな
る。本構造により、高速回転時にも、旋回キー部に作用
する面圧Ｐ及びＰＶ値（Ｖ：摩擦速度）を従来機より低
くせしめ、旋回キー摺動部の摩耗が抑制する効果が得ら
れる。Next, referring to FIG. 10 to FIG. 12, an end plate support seat 11e for supporting the rear part of the outer peripheral part of the end plate of the orbiting scroll 6 and an Oldham key groove part 52m on the frame side are provided above the frame 11 for supporting the main spindle 14 in the central part. The oil sump 57 is formed between the inner peripheral end 58 and the minute protrusion 51. For this reason, even if the compressor is stopped, oil remains in that portion, and in particular, oil is always present in the Oldham key groove 52m. Then, when the compressor is restarted, the deficient oil amount of the conventional machine will not occur. Further, the deterioration of the lubrication performance of the sliding portion of the Oldham mechanism portion due to the insufficient amount of oil is also eliminated, and the reliability of the Oldham mechanism portion can be improved. Further, in FIG. 13, by setting the key area of the Oldham key portion 3a, which is in sliding contact with the key groove portion on the back end portion of the swivel mirror plate, to be larger than the frame side in the Oldham mechanism, the surface pressure acting on the key portion is reduced from the frame side. You can do it.
Further, since the outer dimension Dor 1 of the key portion 3a is made larger than the ring outer diameter Dor 2 of the Oldham ring body 3m, the load acting on the key portion 3a on the turning side is applied to the frame 11a.
It is possible to reduce the load applied to the side key portion 3b. With this structure, the surface pressure P and PV value (V: friction speed) acting on the turning key portion can be made lower than that of the conventional machine even during high-speed rotation, and the effect of suppressing wear of the turning key sliding portion can be obtained.
【０００８】[0008]
【実施例】本発明の実施例を図１から図１６にわたって
示す。図１で、旋回スクロール６の鏡板外周部６ａの背
面部に背圧室３６と旋回スクロール鏡板外周部の側部空
間１１ｆとをシールするシール手段３４を備えた様子を
示す部分断面図である。図２と図３は、旋回スクロール
６の平面図と縦断面図である。図４と図５は、固定スク
ロール５の平面図と縦断面図である。尚、図中実線矢印
は冷媒ガスの流れ方向，破線矢印は油の流れ方向を示
す。図２で、旋回スクロール６の鏡板外周部６ａの背面
外周部にシール手段３４を内包するためのリング溝６ｆ
を備えている。旋回スクロール部材６は円板状の鏡板６
ａと、これに直立し、固定スクロールのラップと同一形
状に形成されたラップ６ｂと、鏡板の反ラップ面に形成
されたボス６ｃからなっている。６ｅ，６ｄは鏡板を貫
通した小さい孔で、６ｙはオルダムキー溝部である。図
１３に示すように、キー溝の長さＬ５は、フレーム側キ
ー溝の長さＬ６（図１１参照）よりオルダムキーの突起
部長さＬ４の分、長く設定している。図４に示すよう
に、背圧室３６と旋回スクロール鏡板の側部空間１１ｆ
と吸入室５ｆとを連通するためスラスト軸受面となる固
定スクロールの鏡板外周面５ｋに放射状溝部５ｒを周上
に満弁に備えている。摺動面５ｋにはフレーム室１１ｆ
から油が供給されてくる。５ｍは、半環状の溝部で吸入
圧力Ｐｓの雰囲気である。図５で、固定スクロール５の
鏡板外周面５ｋには、テーパ形状の溝部５ｚを設けても
よい。摺動面５ｋに油膜による動圧Ｐoil の発生しやす
いテーパ形状とするもので、テーパ形状部５ｚの軸方向
の最大の段差は十数μから数十μの微小な寸法に設定し
てもよい。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment of the present invention is shown in FIGS. FIG. 1 is a partial cross-sectional view showing a state in which a back pressure chamber 36 and a sealing means 34 for sealing a side space 11f of the outer peripheral portion of the orbiting scroll end plate are provided on the back surface of the outer peripheral portion 6a of the orbiting scroll 6 in FIG. 2 and 3 are a plan view and a vertical sectional view of the orbiting scroll 6. 4 and 5 are a plan view and a vertical sectional view of the fixed scroll 5. In the figure, the solid line arrow indicates the flow direction of the refrigerant gas, and the broken line arrow indicates the flow direction of the oil. In FIG. 2, a ring groove 6f for enclosing the sealing means 34 in the outer peripheral surface of the rear surface of the outer peripheral portion 6a of the orbiting scroll 6.
It has. The orbiting scroll member 6 is a disk-shaped end plate 6
a, a wrap 6b which is upright to this and is formed in the same shape as the wrap of the fixed scroll, and a boss 6c formed on the opposite wrap surface of the end plate. 6e and 6d are small holes penetrating the end plate, and 6y is an Oldham key groove. As shown in FIG. 13, the length L5 of the key groove is set longer than the length L6 of the frame side key groove (see FIG. 11) by the length L4 of the protrusion of the Oldham key. As shown in FIG. 4, the back pressure chamber 36 and the side space 11f of the orbiting scroll end plate are shown.
In order to connect the suction chamber 5f with the suction chamber 5f, the outer peripheral surface 5k of the fixed scroll, which serves as the thrust bearing surface, is provided with radial grooves 5r on the circumference to be fully filled. Frame chamber 11f on sliding surface 5k
Oil is supplied from. 5 m is the atmosphere of the suction pressure Ps in the semi-annular groove. In FIG. 5, a tapered groove 5z may be provided on the outer peripheral surface 5k of the fixed scroll 5. The sliding surface 5k is formed into a taper shape in which a dynamic pressure Poil due to an oil film is easily generated, and the maximum step difference in the axial direction of the taper-shaped portion 5z may be set to a minute dimension of a few tens μ to a few tens μ. .
【０００９】図６と図７は、シール手段３４の周辺部の
構造を示す部分縦断面図である。シール手段３４とし
て、シールリング３３を開示している。シールリング３
３の背圧室側に切欠き部３４ａを形成し、フレーム１１
の鏡板支持座１１ｅと対向している。図４に示すよう
に、側部空間１１ｆと吸入室５ｆとが固定スクロール５
の鏡板外周面５ｋに設けた放射状溝部５ｒによって吸入
室５ｆ側に、旋回スクロールの偏心した旋回運動により
スムースに油が排出・移動することになる。また、この
排油がスラスト軸受面となっている固定スクロール５の
鏡板外周面５ｋの潤滑に供される。このため、摺動面で
の油潤滑が確実に行われ、この部分での摺動性能が改善
されひいては摺動損失が低減する。図６に示すように、
旋回スクロール６の鏡板背面のシール手段３４の内側領
域には吐出圧力Ｐｄと吸入圧力Ｐｓとの中間圧力Ｐｍが
作用し、シール手段３４の外側領域は吸入圧力Ｐｓの雰
囲気としている。図７は、シールリング３３の作動を確
実にするため、シールリング３３の背部にバックアップ
リング３７を付加した構造を示す。図８と図９は、バッ
クアップリングの平面図と縦断面図で、板厚が０.２mm
前後でリング高さが１mm前後の波板状で環状に形成して
いる。図１０は、その他の実施例での密閉形スクロール
圧縮機の部分縦断面図である。図１１は、フレーム１１
の平面図である。図１２は、フレーム１１とシール手段
３４の周辺部の構造を示す部分縦断面図である。中央部
の主軸１４を支持するフレームの上方部に旋回スクロー
ルの鏡板外周部の背面部を支える鏡板支持座１１ｅを形
成し、旋回スクロールの自転防止部材としてオルダムリ
ング部およびオルダムキー部よりなるオルダム機構３を
旋回スクロール６とフレーム１１との間に配置してい
る。オルダムリング本体部３ｍが軸方向に対向するフレ
ーム台座面５４に対してフレーム側オルダムキー溝部の
内周端部に１mm前後の微小な突起部５１を備える。図１
２で、鏡板支持座１１ｅの内周部５８とオルダムキー溝
部５２ｍの内周端部５１との間に油溜め部５７を構成し
ている。必然とオルダムキー溝部５２ｍにも油が溜るこ
とになる。また、油溜め部５７に溜った油２２ａがオル
ダムリング本体部３ｍの往復移動に伴い周辺部に飛散
し、油滴２２ｃとなって背圧室内部の摺動部の潤滑に供
される。図１３と図１４は、オルダムリング３の平面図
と縦断面図である。図１３で、オルダム機構３で、旋回
鏡板６ａの背面部にキー溝部６ｙと摺動接触するオルダ
ムキー部３ａの外法寸法Ｄor1 をオルダムリング本体部
のリング外径Ｄor2 より大きくなるように凸部３ｆを備
えている。旋回側オルダムキー３ａの摺動面積は、（Ｌ
１×Ｈ１）の大きさとなる。一方、フレーム側オルダム
キー３ｂの摺動面積は、（Ｌ２×Ｈ２）の大きさとな
り、Ｌ１＞Ｌ２の関係がある。図１５は、オルダムリン
グ３とフレームと旋回スクロール６との係合部の様子を
示す部分縦断面図である。6 and 7 are partial vertical sectional views showing the structure of the peripheral portion of the sealing means 34. The seal ring 33 is disclosed as the sealing means 34. Seal ring 3
3 is formed with a notch 34a on the side of the back pressure chamber,
Of the mirror plate support seat 11e. As shown in FIG. 4, the side space 11f and the suction chamber 5f are fixed scroll 5
Due to the radial grooves 5r provided on the outer peripheral surface 5k of the end plate, the oil is smoothly discharged and moved to the suction chamber 5f side by the eccentric orbiting motion of the orbiting scroll. Further, this drained oil is used to lubricate the outer peripheral surface 5k of the end plate of the fixed scroll 5 serving as the thrust bearing surface. Therefore, oil lubrication on the sliding surface is surely performed, sliding performance in this portion is improved, and sliding loss is reduced. As shown in FIG.
An intermediate pressure Pm between the discharge pressure Pd and the suction pressure Ps acts on the inner area of the sealing means 34 on the rear surface of the end plate of the orbiting scroll 6, and the outer area of the sealing means 34 is set to the atmosphere of the suction pressure Ps. FIG. 7 shows a structure in which a backup ring 37 is added to the back of the seal ring 33 to ensure the operation of the seal ring 33. 8 and 9 are a plan view and a vertical sectional view of the backup ring, with a plate thickness of 0.2 mm.
The front and rear rings are formed in a corrugated plate shape with a ring height of about 1 mm. FIG. 10 is a partial vertical cross-sectional view of a hermetic scroll compressor according to another embodiment. FIG. 11 shows a frame 11
FIG. FIG. 12 is a partial vertical cross-sectional view showing the structure of the peripheral portion of the frame 11 and the sealing means 34. An Oldham mechanism 3 including an Oldham ring portion and an Oldham key portion is formed as an autorotation preventing member of an orbiting scroll by forming an end plate support seat 11e that supports a rear portion of an outer peripheral portion of an orbiting scroll end plate on an upper portion of a frame that supports a main shaft 14 in a central portion. Is arranged between the orbiting scroll 6 and the frame 11. The Oldham ring main body 3m is provided with a minute protrusion 51 of about 1 mm at the inner peripheral end of the frame-side Oldham key groove portion with respect to the frame pedestal surface 54 opposed in the axial direction. FIG.
2, the oil sump portion 57 is formed between the inner peripheral portion 58 of the end plate support seat 11e and the inner peripheral end portion 51 of the Oldham key groove portion 52m. Inevitably, oil collects also in the Oldham key groove 52m. Further, the oil 22a accumulated in the oil sump 57 is scattered to the peripheral portion as the Oldham ring main body 3m reciprocates, and becomes an oil drop 22c, which is used to lubricate the sliding portion inside the back pressure chamber. 13 and 14 are a plan view and a vertical sectional view of the Oldham ring 3. In FIG. 13, in the Oldham mechanism 3, the outside dimension Dor 1 of the Oldham key portion 3a that is in sliding contact with the key groove portion 6y on the back surface of the swivel end plate 6a is convex so as to be larger than the ring outer diameter Dor 2 of the Oldham ring main body portion. It is provided with a part 3f. The sliding area of the turning Oldham key 3a is (L
The size is 1 × H1). On the other hand, the sliding area of the frame-side Oldham key 3b has a size of (L2 × H2), and has a relationship of L1> L2. FIG. 15 is a partial vertical cross-sectional view showing a state of an engaging portion between the Oldham ring 3, the frame and the orbiting scroll 6.
【００１０】図１６は、図１５と図７の実施例を密閉形
スクロール圧縮機に組み込んだ場合の全体構成を示す縦
断面図である。図１６に示すように、密閉容器２内の上
方に圧縮機部１００が、下方に電動機部３が収納されて
いる。そして、密閉容器２内は上部室１ａ（吐出室）と
電動機室１ｂ，１ｃとに区画されている。FIG. 16 is a vertical cross-sectional view showing the overall construction when the embodiment of FIGS. 15 and 7 is incorporated in a hermetic scroll compressor. As shown in FIG. 16, the compressor unit 100 is housed in the upper portion of the closed container 2, and the electric motor unit 3 is housed in the lower portion. Then, the inside of the closed container 2 is divided into an upper chamber 1a (discharge chamber) and electric motor chambers 1b and 1c.
【００１１】圧縮機部１００は固定スクロール部材５と
旋回スクロール部材６を互いに噛合せて圧縮室（密閉空
間）８を形成している。固定スクロール部材５は、円板
状の鏡板５ａと、これに直立しインボリュート曲線ある
いはこれに近似の曲線に形成されたラップ５ｂとからな
り、その中心部に吐出口１０，外周部に吸入口１６を備
えている。フレーム１１は中央部に軸受部を形成し、こ
の軸受部に回転軸１４が支承され、回転軸先端の偏心軸
１４ａは、ボス６ｃに旋回運動が可能なように挿入され
ている。またフレーム１１には固定スクロール部材５が
複数本のボルトによって固定され、旋回スクロール部材
６はオルダムリングおよびオルダムキーよりなるオルダ
ム機構３によってフレーム１１に支承され、旋回スクロ
ール部材６は固定スクロール部材５に対して、自転しな
いで旋回運動をするように形成されている。回転軸１４
には下部に、ロータ３ｂに固定された電動機軸１４ｂを
一体に連設し、電動機部３を直結している。固定スクロ
ール部材５の吸入口１６には密閉容器２を貫通して垂直
方向の吸入管１７が接続され、吐出口１０が開口してい
る上部室１ａは通路１８ａ，１８ｂを介して上部電動機
室１ｂと連通している。この上部電動室１ｂは電動機ス
テータ３ａと密閉容器１側壁との間の通路２５を介して
下部電動機室１ｃに連通している。また上部電動機室１
ｂは密閉容器２を貫通する吐出管２０に連通している。In the compressor section 100, a fixed scroll member 5 and an orbiting scroll member 6 are meshed with each other to form a compression chamber (closed space) 8. The fixed scroll member 5 is composed of a disk-shaped end plate 5a and a wrap 5b which stands upright on the end plate 5a and is formed in an involute curve or a curve similar to this, and has a discharge port 10 at the center thereof and an intake port 16 at the outer peripheral portion thereof. Is equipped with. The frame 11 has a bearing portion formed in the center thereof, and the rotary shaft 14 is supported by the bearing portion, and the eccentric shaft 14a at the tip of the rotary shaft is inserted into the boss 6c so as to be capable of turning motion. The fixed scroll member 5 is fixed to the frame 11 by a plurality of bolts, the orbiting scroll member 6 is supported by the frame 11 by the Oldham mechanism 3 including an Oldham ring and an Oldham key, and the orbiting scroll member 6 is fixed to the fixed scroll member 5. Thus, it is formed so as to make a turning motion without rotating. Rotating shaft 14
An electric motor shaft 14b fixed to the rotor 3b is integrally connected to the lower part of the electric motor unit 3 to directly connect the electric motor unit 3. A vertical suction pipe 17 is connected to the suction port 16 of the fixed scroll member 5 through the closed container 2, and the upper chamber 1a in which the discharge port 10 is opened has an upper motor chamber 1b through passages 18a and 18b. Is in communication with. The upper electric motor chamber 1b communicates with the lower electric motor chamber 1c via a passage 25 between the electric motor stator 3a and the side wall of the closed casing 1. Also the upper motor room 1
b communicates with a discharge pipe 20 penetrating the closed container 2.
【００１２】なお、２２は密閉容器底部の油溜りを示
す。潤滑油２２ａは、密閉容器２の下部に油溜り２２と
して溜められる。回転軸１４の下端は偏心軸部(クラン
クピン)１４ａを備え、偏心軸部１４ａが旋回スクロー
ル６の鏡板６ａのボス部６ｃ内の旋回軸受３２を介し
て、スクロール圧縮要素部である旋回スクロール６と係
合している。回転軸１４には、各軸受部への給油を行う
ための中心縦孔１３が回転軸１４の下端から上端面まで
形成される。２３は、回転軸１４の下端と底部油溜り２
２を連ねる揚油管である。偏心軸部１４ａの下部には、
旋回スクロール６のボス部６ｃの先端面と対向して主軸
受４０があり、その下部の電動機室１ｂにバランスウエ
イト９ａが回転軸１４と結合し一体化して形成されてい
る。潤滑油22ａの油溜り２２内に浸漬けされた揚油管２
３の下端は高圧の吐出圧力Ｐｄを受けており、一方、下
流となる旋回軸受３１（図１０参照）及び主軸受（すべ
り軸受４０）のまわりは、旋回鏡板６ａに設けた細孔６
ｄ，６ｅ（図２参照）により圧縮途中の圧力である中間
圧力Ｐｍを受けているため、（Ｐｄ−Ｐｍ）の圧力差に
よって、容器底部の油溜り２２中の潤滑油２２ａは、中
心縦孔１３内を上昇する。Reference numeral 22 denotes an oil sump at the bottom of the closed container. The lubricating oil 22a is stored in the lower part of the closed container 2 as an oil sump 22. The lower end of the rotating shaft 14 is provided with an eccentric shaft portion (crank pin) 14a, and the eccentric shaft portion 14a is a scroll compression element portion via the orbiting bearing 32 in the boss portion 6c of the end plate 6a of the orbiting scroll 6. Is engaged with. A central vertical hole 13 for supplying oil to each bearing is formed in the rotary shaft 14 from the lower end to the upper end surface of the rotary shaft 14. 23 is a lower end of the rotary shaft 14 and a bottom oil sump 2
It is a pumping oil pipe that connects two. At the bottom of the eccentric shaft portion 14a,
There is a main bearing 40 facing the tip surface of the boss portion 6c of the orbiting scroll 6, and a balance weight 9a is formed integrally with the rotary shaft 14 in the electric motor chamber 1b below the main bearing 40. Oil pump 2 immersed in oil sump 22 of lubricating oil 22a
The lower end of 3 receives the high discharge pressure Pd, while the swirl bearing 31 (see FIG. 10) and the main bearing (sliding bearing 40), which are located downstream, are surrounded by the pores 6 formed in the swirl end plate 6a.
Since the intermediate pressure Pm, which is the pressure in the middle of compression, is received by d and 6e (see FIG. 2), the lubricating oil 22a in the oil sump 22 at the bottom of the container is urged by the central vertical hole due to the pressure difference of (Pd-Pm). Ascend in 13.
【００１３】このように、各軸受部への給油を、中心縦
孔給油による差圧給油法によって行う。As described above, the oil is supplied to each bearing by the differential pressure oil supply method using the central vertical hole oil supply.
【００１４】中心縦孔１３内を上昇した潤滑油２２ａ
は、主軸受４０ａ及び旋回軸受３１へ給油される。それ
ら軸受部３１，４０に給油された油は、背圧室３６に流
入する。なお、背圧室３６に流入した油はオルダムリン
グ部３周辺部を潤滑するとともに、冷媒ガスと混合し、
ひいては、背圧孔６ｄ（図２参照）を介して圧縮室８に
流出する。圧縮室８に至った油は、冷媒ガスとともに加
圧され、吐出口１０を介して固定スクロール５上方の吐
出室１ａさらに電動機室１ｂへと移動する。この吐出室
１ａと電動機室１ｂとで主に冷媒ガスと油は分離され、
油は密閉容器２の下部の油溜り２２に落下し、再び各摺
動部に供給される。このような油の流れとすることによ
り、圧縮機各部での潤滑が確実に行われる。図１６で、
効率向上に効果のある主な構造は、（１）鏡板背面シー
ル構造、（２）バランスウェイト外置き構造、（３）旋
回スクロール鏡板外周部の油封じ込み防止構造、（４）
モータの下方に下軸受４４を配置した構造等である。項
目（１）の「鏡板背面シール構造」とは、旋回スクロー
ル鏡板の背面部にシールリングを配置し、主軸内を通っ
て軸受部に供給された油が背圧室を介して、フレーム室
１１ｆに流入するのを防止した構造である。その項目
（１）と項目（２）（３）は、従来機に対して油撹拌防
止を狙った構造となる。また、項目（４）は、下軸受部
４４に自動調心球面ガイド軸受４４ａを適用し、主軸１
４の片当たりを防止している。Lubricating oil 22a rising in the central vertical hole 13
Is supplied to the main bearing 40a and the slewing bearing 31. The oil supplied to the bearing portions 31 and 40 flows into the back pressure chamber 36. The oil flowing into the back pressure chamber 36 lubricates the peripheral part of the Oldham ring part 3 and mixes with the refrigerant gas,
Eventually, it flows out into the compression chamber 8 through the back pressure hole 6d (see FIG. 2). The oil that has reached the compression chamber 8 is pressurized together with the refrigerant gas and moves through the discharge port 10 to the discharge chamber 1a above the fixed scroll 5 and further to the electric motor chamber 1b. Refrigerant gas and oil are mainly separated in the discharge chamber 1a and the electric motor chamber 1b,
The oil drops into the oil sump 22 at the bottom of the closed container 2 and is supplied again to each sliding portion. Such an oil flow ensures reliable lubrication in each part of the compressor. In FIG.
The main structures that are effective in improving efficiency are: (1) End plate backside seal structure, (2) Balance weight external structure, (3) Orbiting scroll end plate outer periphery oil containment prevention structure, (4)
For example, the lower bearing 44 is arranged below the motor. Item (1) "End plate back seal structure" means that a seal ring is arranged on the back part of the orbiting scroll end plate, and the oil supplied to the bearing through the main shaft passes through the back pressure chamber to the frame chamber 11f. It has a structure that prevents it from flowing into. The items (1) and (2) and (3) have a structure aimed at preventing oil agitation in the conventional machine. Item (4) applies the self-aligning spherical guide bearing 44a to the lower bearing portion 44, and
It prevents the uneven contact of 4.
【００１５】[0015]
【発明の効果】本発明によれば次の効果がある。The present invention has the following effects.
【００１６】（１）旋回スクロール６の鏡板外周部６ａ
の側部空間１１ｆにおける油撹拌損失を大きく低減でき
るとともに、シール手段３４を備えた構成により、旋回
スクロール６の鏡板外径を縮小化ができる。このため、
圧縮機外径も小型化と軽量化が図れる。(1) End plate outer peripheral portion 6a of the orbiting scroll 6
The oil stirring loss in the side space 11f can be greatly reduced, and the outer diameter of the end plate of the orbiting scroll 6 can be reduced by the configuration including the sealing means 34. For this reason,
The outer diameter of the compressor can also be reduced in size and weight.
【００１７】（２）スラスト軸受面となっている固定ス
クロール５の鏡板外周面５ｋの潤滑性能面では、摺動面
での油潤滑が確実に行われ、この部分での摺動性能が改
善されひいては摺動損失が低減する。（１）項目の効果
と併せて、圧縮機の性能と信頼性を大幅に向上でき、年
間を通して空調機の消費電力が大きく低減できる。(2) On the lubrication performance surface of the end plate outer peripheral surface 5k of the fixed scroll 5 serving as the thrust bearing surface, oil lubrication is reliably performed on the sliding surface, and the sliding performance at this portion is improved. As a result, sliding loss is reduced. In addition to the effect of item (1), the performance and reliability of the compressor can be significantly improved, and the power consumption of the air conditioner can be greatly reduced throughout the year.
【００１８】（３）旋回スクロール６の鏡板背面のシー
ル手段３４の内側領域には吐出圧力Ｐｄと吸入圧力Ｐｓ
との中間である中間圧力Ｐｍが作用し、シール手段３４
の外側領域は吸入圧力Ｐｓの雰囲気にしているため、背
圧室の圧力Ｐｍが、従来機に対して低く設定が可能とな
り、軸受給油限界圧力比が拡大される。(3) The discharge pressure Pd and the suction pressure Ps are provided in the inner region of the sealing means 34 on the rear surface of the end plate of the orbiting scroll 6.
And an intermediate pressure Pm that is intermediate between
Since the outside region of is in the atmosphere of the suction pressure Ps, the back pressure chamber pressure Pm can be set lower than that of the conventional machine, and the bearing oil supply limit pressure ratio is expanded.
【００１９】（４）側部空間１１ｆ（フレーム室）から
吸入室５ｆへの高温の油もれを大きく防止できるので、
吸入ガスの内部加熱量を軽減でき、吸入ガスの内部加熱
量低下による体積効率が向上できる。この効果は、軸受
油量が増加して吸入ガスの内部加熱量が増加する高圧力
比での運転条件で顕著となる。(4) Since high temperature oil leakage from the side space 11f (frame chamber) to the suction chamber 5f can be largely prevented,
The internal heating amount of the intake gas can be reduced, and the volumetric efficiency can be improved by reducing the internal heating amount of the intake gas. This effect becomes remarkable under the operating conditions at a high pressure ratio in which the amount of bearing oil increases and the amount of internal heating of the intake gas increases.
【００２０】（５）圧縮機が停止されてもオルダムキー
溝部５２ｍには常に油が有り、圧縮機の再起動時には、
従来機のような油量不足が生じることがなくなる。そし
て、油量不足によるオルダム機構部の摺動部の潤滑性能
が損なわれることも解消され、オルダム機構周辺部の信
頼性が向上できる。(5) Even if the compressor is stopped, there is always oil in the Oldham key groove 52m, and when the compressor is restarted,
There will be no shortage of oil as in conventional machines. Then, the deterioration of the lubrication performance of the sliding part of the Oldham mechanism due to the insufficient amount of oil is also eliminated, and the reliability of the peripheral part of the Oldham mechanism can be improved.
【００２１】（６）オルダム機構で、旋回鏡板背面部の
キー溝部と摺動接触するオルダムキー部３ａのキー面積
をフレーム側より大きく設定することで、キー部に作用
する面圧をフレーム側より低減できることになる。ま
た、そのキー部３ａの外法寸法Ｄor1をオルダムリング
本体部３ｍのリング外径Ｄor2より大きくしているの
で、旋回側のキー部３ａに作用する荷重をフレーム１１
側のキー部３ｂに作用する荷重より軽減できることにな
る。本構造により、高速回転時でも、旋回キー部に作用
する面圧Ｐ及びＰＶ値を従来機より低くせしめ、旋回キ
ー摺動部の摩耗が抑制する効果が得られる。(6) With the Oldham mechanism, by setting the key area of the Oldham key portion 3a which is in sliding contact with the key groove portion on the rear surface of the swing end plate to be larger than that on the frame side, the surface pressure acting on the key portion is reduced from that on the frame side. You can do it. Further, since the outer dimension Dor 1 of the key portion 3a is made larger than the ring outer diameter Dor 2 of the Oldham ring body 3m, the load acting on the key portion 3a on the turning side is applied to the frame 11a.
It is possible to reduce the load applied to the side key portion 3b. With this structure, the surface pressures P and PV acting on the turning key portion can be made lower than those of the conventional machine even during high-speed rotation, and the effect of suppressing wear of the turning key sliding portion can be obtained.
【図１】密閉形スクロール圧縮機の部分縦断面図。FIG. 1 is a partial vertical cross-sectional view of a hermetic scroll compressor.
【図２】旋回スクロール６の平面図。FIG. 2 is a plan view of an orbiting scroll 6.
【図３】旋回スクロール６の縦断面図。FIG. 3 is a vertical sectional view of an orbiting scroll 6.
【図４】固定スクロール５の平面図。FIG. 4 is a plan view of a fixed scroll 5.
【図５】固定スクロール５の縦断面図。FIG. 5 is a vertical sectional view of a fixed scroll 5.
【図６】シール手段３４の周辺部の構造を示す部分縦断
面図。FIG. 6 is a partial vertical cross-sectional view showing the structure of the peripheral portion of the sealing means 34.
【図７】シール手段３４の周辺部の構造を示す部分縦断
面図。FIG. 7 is a partial vertical cross-sectional view showing the structure of the peripheral portion of the sealing means 34.
【図８】バックアップリングの平面図。FIG. 8 is a plan view of a backup ring.
【図８】バックアップリングの縦断面図。FIG. 8 is a vertical sectional view of a backup ring.
【図１０】その他の実施例での密閉形スクロール圧縮機
の部分縦断面図。FIG. 10 is a partial vertical cross-sectional view of a hermetic scroll compressor according to another embodiment.
【図１１】フレーム１１の平面図。FIG. 11 is a plan view of the frame 11.
【図１２】フレーム１１とシール手段３４の周辺部の構
造を示す部分縦断面図。FIG. 12 is a partial vertical cross-sectional view showing the structure of the peripheral portion of the frame 11 and the sealing means 34.
【図１３】オルダムリング３の平面図。FIG. 13 is a plan view of the Oldham ring 3.
【図１４】オルダムリング３の縦断面図。FIG. 14 is a vertical cross-sectional view of the Oldham ring 3.
【図１５】オルダムリング３とフレームと旋回スクロー
ル６との係合部の様子を示す部分縦断面図。FIG. 15 is a partial vertical cross-sectional view showing a state of an engaging portion between the Oldham ring 3, the frame, and the orbiting scroll 6.
【図１６】本発明の全体構成を示す密閉形スクロール圧
縮機の縦断面図。FIG. 16 is a vertical cross-sectional view of a hermetic scroll compressor showing the overall configuration of the present invention.
２…密閉容器、３…オルダムリング、５…固定スクロー
ル、５ａ，６ａ…スクロール鏡板部、６…旋回スクロー
ル、８…圧縮室、１１…フレーム、１４…主軸（クラン
ク軸）、１８…連通路、２２…油溜り、３４…シール手
段、３６…背圧室、４０…主軸受、５１…フレーム突起
部。2 ... Airtight container, 3 ... Oldham ring, 5 ... Fixed scroll, 5a, 6a ... Scroll end plate part, 6 ... Orbiting scroll, 8 ... Compression chamber, 11 ... Frame, 14 ... Main shaft (crank shaft), 18 ... Communication passage, 22 ... Oil sump, 34 ... Sealing means, 36 ... Back pressure chamber, 40 ... Main bearing, 51 ... Frame protrusion.
─────────────────────────────────────────────────────
─────────────────────────────────────────────────── ───
【手続補正書】[Procedure amendment]
【提出日】平成７年８月７日[Submission date] August 7, 1995
【手続補正１】[Procedure Amendment 1]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】図面の簡単な説明[Name of item to be corrected] Brief description of the drawing
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【図面の簡単な説明】[Brief description of drawings]
【図１】密閉形スクロール圧縮機の部分縦断面図。FIG. 1 is a partial vertical cross-sectional view of a hermetic scroll compressor.
【図２】旋回スクロール６の平面図。FIG. 2 is a plan view of an orbiting scroll 6.
【図３】旋回スクロール６の縦断面図。FIG. 3 is a vertical sectional view of an orbiting scroll 6.
【図４】固定スクロール５の平面図。FIG. 4 is a plan view of a fixed scroll 5.
【図５】固定スクロール５の縦断面図。FIG. 5 is a vertical sectional view of a fixed scroll 5.
【図６】シール手段３４の周辺部の構造を示す部分縦断
面図。FIG. 6 is a partial vertical cross-sectional view showing the structure of the peripheral portion of the sealing means 34.
【図７】シール手段３４の周辺部の構造を示す部分縦断
面図。FIG. 7 is a partial vertical cross-sectional view showing the structure of the peripheral portion of the sealing means 34.
【図８】バックアップリングの平面図。FIG. 8 is a plan view of a backup ring.
【図９】バックアップリングの縦断面図。FIG. 9 is a vertical sectional view of a backup ring.
【図１０】その他の実施例での密閉形スクロール圧縮機
の部分縦断面図。FIG. 10 is a partial vertical cross-sectional view of a hermetic scroll compressor according to another embodiment.
【図１１】フレーム１１の平面図。FIG. 11 is a plan view of the frame 11.
【図１２】フレーム１１とシール手段３４の周辺部の構
造を示す部分縦断面図。FIG. 12 is a partial vertical cross-sectional view showing the structure of the peripheral portion of the frame 11 and the sealing means 34.
【図１３】オルダムリング３の平面図。FIG. 13 is a plan view of the Oldham ring 3.
【図１４】オルダムリング３の縦断面図。FIG. 14 is a vertical cross-sectional view of the Oldham ring 3.
【図１５】オルダムリング３とフレームと旋回スクロー
ル６との係合部の様子を示す部分縦断面図。FIG. 15 is a partial vertical cross-sectional view showing a state of an engaging portion between the Oldham ring 3, the frame, and the orbiting scroll 6.
【図１６】本発明の全体構成を示す密閉形スクロール圧
縮機の縦断面図。FIG. 16 is a vertical cross-sectional view of a hermetic scroll compressor showing the overall configuration of the present invention.
【符号の説明】 ２…密閉容器、３…オルダムリング、５…固定スクロー
ル、５ａ，６ａ…スクロール鏡板部、６…旋回スクロー
ル、８…圧縮室、１１…フレーム、１４…主軸（クラン
ク軸）、１８…連通路、２２…油溜り、３４…シール手
段、３６…背圧室、４０…主軸受、５１…フレーム突起
部。[Explanation of Codes] 2 ... Airtight container, 3 ... Oldham ring, 5 ... Fixed scroll, 5a, 6a ... Scroll end plate part, 6 ... Orbiting scroll, 8 ... Compression chamber, 11 ... Frame, 14 ... Main shaft (crank shaft), Reference numeral 18 ... Communication passage, 22 ... Oil sump, 34 ... Sealing means, 36 ... Back pressure chamber, 40 ... Main bearing, 51 ... Frame protrusion.
Claims (3)
を主軸を介して連設して収納し、密容器室をフレームで
上下室に区画し、前記スクロール圧縮機は、円板状鏡板
に渦巻状のラップを直立する固定スクロール部材及び旋
回スクロール部材を、ラップを内側にして噛合せ、前記
旋回スクロール部材を主軸に連設する偏心軸部に係合
し、前記旋回スクロール部材を自転することなく前記固
定スクロール部材に対し旋回運動させ、前記固定スクロ
ール部材には中心部に開口する吐出口と外周部に開口す
る吸入口を設け、前記吸入口よりガスを吸入し、前記両
スクロール部材で形成される圧縮空間を中心に移動させ
容積を減少してガスを圧縮し、吐出口より圧縮ガスを上
部容器室に吐出し、通路を介し下部容器室に導き、吐出
管を介し器外に吐出するスクロール圧縮機において、前
記旋回スクロールの鏡板外周部の背面部に背圧室と前記
旋回スクロール鏡板外周部の側部空間とをシールするシ
ール手段を備え、前記側部空間と吸入室とを連通するた
めスラスト軸受面となる前記固定スクロールの鏡板外周
面に放射状溝部を備えることを特徴とするスクロール圧
縮機。1. A scroll compressor and an electric motor are connected in series through a main shaft in a hermetic container and housed therein, and a hermetic container chamber is divided into an upper chamber and a lower chamber by a frame. The scroll compressor is a disc-shaped end plate. To rotate the orbiting scroll member by rotating a fixed scroll member and an orbiting scroll member, which stand upright of a spiral wrap, with the wrap being inwardly meshed with each other, and engaging the orbiting scroll member with an eccentric shaft portion continuous with the main shaft. The fixed scroll member is swung with respect to the fixed scroll member, and the fixed scroll member is provided with a discharge port that opens in the center and an intake port that opens in the outer periphery. Compressed gas is discharged from the discharge port to the upper container chamber, guided to the lower container chamber through the passage, and discharged outside the device through the discharge pipe. In the scroll compressor according to the first aspect of the invention, a sealing means for sealing a back pressure chamber and a side space of the outer peripheral portion of the orbiting scroll end plate is provided on the back surface of the outer peripheral portion of the orbiting scroll, and the side space and the suction chamber are communicated with each other. Therefore, the scroll compressor is provided with radial groove portions on the outer peripheral surface of the end plate of the fixed scroll which serves as a thrust bearing surface.
定スクロール部材及び旋回スクロール部材を、ラップを
内側にして噛合せ、前記旋回スクロール部材を主軸に連
設する偏心軸部に係合し、前記旋回スクロール部材を自
転することなく前記固定スクロール部材に対し旋回運動
させ、前記固定スクロール部材には中心部に開口する吐
出口と外周部に開口する吸入口を設け、前記吸入口より
ガスを吸入し、前記両スクロール部材で形成される圧縮
空間を中心に移動させ容積を減少してガスを圧縮し、吐
出口より圧縮ガスを吐出するスクロール圧縮機におい
て、中央部の前記主軸を支持するフレームの上方部に前
記旋回スクロールの鏡板外周部の背面部を支える鏡板支
持座を形成し、前記旋回スクロールの自転防止部材とし
てオルダムリング部およびオルダムキー部よりなるオル
ダム機構を前記旋回スクロールとフレームとの間に配置
し、オルダムリング本体部が軸方向に対向するフレーム
台座面に対してフレーム側オルダムキー溝部の内周端部
に突起部を備え、前記鏡板支持座の内周部と前記オルダ
ムキー溝部の内周端部との間に油溜め部を構成したこと
を特徴とするスクロール圧縮機。2. A fixed scroll member and an orbiting scroll member, which stand upright with a spiral wrap on a disk-shaped end plate, are engaged with each other with the wrap inside, and are engaged with an eccentric shaft portion that connects the orbiting scroll member to a main shaft. Then, the orbiting scroll member is orbitally moved with respect to the fixed scroll member without rotating, and the fixed scroll member is provided with a discharge port opening at the center and an intake port opening at the outer peripheral part, and gas is supplied from the intake port. In the scroll compressor that sucks in, moves around the compression space formed by the scroll members to reduce the volume, compresses the gas, and discharges the compressed gas from the discharge port, the main shaft of the central portion is supported. An end plate support seat for supporting the rear surface of the outer peripheral portion of the orbiting scroll of the orbiting scroll is formed in the upper part of the frame, and the Oldham ring portion is provided as a rotation preventing member of the orbiting scroll. And an Oldham mechanism composed of an Oldham key portion is arranged between the orbiting scroll and the frame, and the Oldham ring main body portion is provided with a protrusion at the inner peripheral end portion of the frame-side Oldham key groove portion with respect to the frame pedestal surface facing in the axial direction. A scroll compressor, wherein an oil sump portion is formed between an inner peripheral portion of the end plate support seat and an inner peripheral end portion of the Oldham key groove portion.
定スクロール部材及び旋回スクロール部材を、ラップを
内側にして噛合せ、前記旋回スクロール部材を主軸に連
設する偏心軸部に係合し、前記旋回スクロール部材を自
転することなく前記固定スクロール部材に対し旋回運動
させ、前記固定スクロール部材には中心部に開口する吐
出口と外周部に開口する吸入口を設け、前記吸入口より
ガスを吸入し、前記両スクロール部材で形成される圧縮
空間を中心に移動させ容積を減少してガスを圧縮し、吐
出口より圧縮ガスを吐出するスクロール圧縮機におい
て、前記旋回スクロールの自転防止部材として円形状の
オルダムリング部とオルダムキー部よりなるオルダム機
構を旋回スクロールとフレームとの間に配置し、旋回鏡
板背面部にキー溝部と摺動接触する前記オルダムキー部
の外法寸法をオルダムリング本体部のリング外径より大
きくなるように凸部を備え、旋回側オルダムキー凸部の
外径がフレーム側キー溝部と摺動接触する前記オルダム
キー部の外法寸法より大きく設定したことを特徴とする
スクロール圧縮機。3. A fixed scroll member and an orbiting scroll member, which stand upright with a spiral wrap on a disk-shaped end plate, are engaged with each other with the wrap inside, and are engaged with an eccentric shaft portion that connects the orbiting scroll member to a main shaft. Then, the orbiting scroll member is orbitally moved with respect to the fixed scroll member without rotating, and the fixed scroll member is provided with a discharge port opening at the center and an intake port opening at the outer peripheral part, and gas is supplied from the intake port. In a scroll compressor that sucks in, compresses gas by moving it around a compression space formed by both scroll members to reduce the volume, and discharges compressed gas from a discharge port, as a rotation preventing member for the orbiting scroll. An Oldham mechanism consisting of a circular Oldham ring and an Oldham key is placed between the orbiting scroll and the frame, and the keyway is formed on the back of the orbiting end plate. The Oldham key is provided with a convex portion so that the outer dimension of the Oldham key portion in sliding contact is larger than the ring outer diameter of the Oldham ring body, and the outer diameter of the swivel Oldham key convex portion is in sliding contact with the frame key groove portion. A scroll compressor characterized by being set larger than the outer dimension of the part.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP08667295A JP3584533B2 (en) | 1995-04-12 | 1995-04-12 | Scroll compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP08667295A JP3584533B2 (en) | 1995-04-12 | 1995-04-12 | Scroll compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH08284853A true JPH08284853A (en) | 1996-10-29 |
| JP3584533B2 JP3584533B2 (en) | 2004-11-04 |
Family
ID=13893532
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP08667295A Expired - Fee Related JP3584533B2 (en) | 1995-04-12 | 1995-04-12 | Scroll compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3584533B2 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008138597A (en) * | 2006-12-01 | 2008-06-19 | Denso Corp | Scroll compressor |
| CN102588286A (en) * | 2011-01-13 | 2012-07-18 | 珠海格力节能环保制冷技术研究中心有限公司 | Vortex compressor sealing structure and vortex compressor containing same |
| JP2013234666A (en) * | 2012-05-09 | 2013-11-21 | Visteon Global Technologies Inc | Refrigerant scroll compressor for air-conditioning system for automobile |
| JP2019190383A (en) * | 2018-04-25 | 2019-10-31 | 三菱重工サーマルシステムズ株式会社 | Oldham ring and scroll compressor |
| WO2019240134A1 (en) * | 2018-06-11 | 2019-12-19 | ダイキン工業株式会社 | Scroll compressor |
| CN114829776A (en) * | 2019-12-20 | 2022-07-29 | 松下知识产权经营株式会社 | Scroll compressor having a discharge port |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5817760B2 (en) | 2013-03-04 | 2015-11-18 | 株式会社豊田自動織機 | Scroll compressor |
-
1995
- 1995-04-12 JP JP08667295A patent/JP3584533B2/en not_active Expired - Fee Related
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008138597A (en) * | 2006-12-01 | 2008-06-19 | Denso Corp | Scroll compressor |
| CN102588286A (en) * | 2011-01-13 | 2012-07-18 | 珠海格力节能环保制冷技术研究中心有限公司 | Vortex compressor sealing structure and vortex compressor containing same |
| JP2013234666A (en) * | 2012-05-09 | 2013-11-21 | Visteon Global Technologies Inc | Refrigerant scroll compressor for air-conditioning system for automobile |
| JP2019190383A (en) * | 2018-04-25 | 2019-10-31 | 三菱重工サーマルシステムズ株式会社 | Oldham ring and scroll compressor |
| WO2019208075A1 (en) * | 2018-04-25 | 2019-10-31 | 三菱重工サーマルシステムズ株式会社 | Oldham ring and scroll compressor |
| AU2019258375B2 (en) * | 2018-04-25 | 2022-03-03 | Mitsubishi Heavy Industries Thermal Systems, Ltd. | Oldham ring and scroll compressor |
| WO2019240134A1 (en) * | 2018-06-11 | 2019-12-19 | ダイキン工業株式会社 | Scroll compressor |
| CN112189096A (en) * | 2018-06-11 | 2021-01-05 | 大金工业株式会社 | Scroll compressor having a discharge port |
| JPWO2019240134A1 (en) * | 2018-06-11 | 2021-05-13 | ダイキン工業株式会社 | Scroll compressor |
| CN114829776A (en) * | 2019-12-20 | 2022-07-29 | 松下知识产权经营株式会社 | Scroll compressor having a discharge port |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3584533B2 (en) | 2004-11-04 |
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