JPH0245672A - Scroll fluid machine - Google Patents
Scroll fluid machineInfo
- Publication number
- JPH0245672A JPH0245672A JP19689688A JP19689688A JPH0245672A JP H0245672 A JPH0245672 A JP H0245672A JP 19689688 A JP19689688 A JP 19689688A JP 19689688 A JP19689688 A JP 19689688A JP H0245672 A JPH0245672 A JP H0245672A
- Authority
- JP
- Japan
- Prior art keywords
- scroll
- receiving groove
- shaft
- swivel
- drive shaft
- 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.)
- Pending
Links
- 239000012530 fluid Substances 0.000 title claims description 31
- 125000006850 spacer group Chemical group 0.000 abstract description 7
- 230000007423 decrease Effects 0.000 abstract description 2
- 230000003247 decreasing effect Effects 0.000 abstract 1
- 230000006835 compression Effects 0.000 description 10
- 238000007906 compression Methods 0.000 description 10
- 239000003921 oil Substances 0.000 description 8
- 238000010586 diagram Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 4
- 239000010687 lubricating oil Substances 0.000 description 4
- 230000010355 oscillation Effects 0.000 description 4
- 239000007788 liquid Substances 0.000 description 3
- 235000007516 Chrysanthemum Nutrition 0.000 description 1
- 244000189548 Chrysanthemum x morifolium Species 0.000 description 1
- 241000283074 Equus asinus Species 0.000 description 1
- 239000000872 buffer Substances 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
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
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/102—Adjustment of the interstices between moving and fixed parts of the machine by means other than fluid pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Rotary Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明はスクロール流体機械、特に振動・騒音を少な
くしてリリーフ機能を備え、信頼性を向上させtスクロ
ール流体機械に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to a scroll fluid machine, and particularly to a t-scroll fluid machine that reduces vibration and noise, has a relief function, and improves reliability.
まず最初に、スクロール流体機械の原理について説明す
る。スクロール流体機械は、二つの渦巻体を相対運動さ
せることにより流体の容積全変化させるものであり、第
4図に圧縮機として用いt場合の動作原理図を示す。こ
の種のスクロール圧縮機は、既に多くの文献や特許公報
に開示され、その原理はよく知られている。First, the principle of a scroll fluid machine will be explained. A scroll fluid machine changes the total volume of fluid by moving two spiral bodies relative to each other, and FIG. 4 shows the principle of operation when used as a compressor. This type of scroll compressor has already been disclosed in many documents and patent publications, and its principle is well known.
第4図は、例えば三菱電機技報(vat、 58.NO
・5゜1984、 pp、 367〜371)に記載さ
れているものであり、図に2いて、αQは空間に対して
靜止しt渦巻体會持つ固定スクロール、■は固定スクロ
ールの渦巻体と噛み合わされ九渦巻体を持ち、その姿勢
を空間に対して変化させない回転運動、すなわち揺動運
動を所定のクランク半径(揺動半径)で行う揺動スクロ
ールである。これら固定スクロールαQ及び揺動スクロ
ールのは同一形状の渦1体で構成されて2す、その形体
は従来から知られている工すに、インボリュートあるい
は円弧等全組み合ワせ友ものである。菊は上記の揺動運
動により流体を圧縮する圧縮室、unri圧縮され九流
体を吐出する吐出口である。ここで、両スクロールが第
4図のlal 、 ibl 、 fat 、 ldlの
Lうに運動すれば、両スクロールの間に形成される三日
月状の圧縮室140は順次その容積勿減じるので、圧m
室(俄に取り込まれた流体は圧縮されて吐出ロバ1)か
ら吐出される。Figure 4 shows, for example, the Mitsubishi Electric Technical Report (VAT, 58.NO
・5゜1984, pp. 367-371), and in Figure 2, αQ is a fixed scroll that is stationary with respect to space and has a spiral body, and ■ is a fixed scroll that meshes with the spiral body of the fixed scroll. It is an oscillating scroll that has nine spiral bodies and performs rotational movement, that is, oscillating movement, at a predetermined crank radius (oscillating radius) without changing its attitude with respect to space. The fixed scroll αQ and the oscillating scroll are composed of a single vortex having the same shape, and the shape thereof is a combination of conventionally known techniques such as an involute or a circular arc. The chrysanthemum is a compression chamber that compresses fluid by the above-mentioned rocking motion, and a discharge port that discharges uncompressed fluid. Here, if both scrolls move in the directions of lal, ibl, fat, and ldl in FIG.
The fluid suddenly taken in is compressed and discharged from the chamber (discharge donkey 1).
以上がスクロール流体機械の動作原理である。第5図は
従来のスクロール流体機械?圧縮機として用いt基本的
なも誇修断面金示す図であり、第6図にその主要部の拡
大断面ケ示す図である。両図Vc′s?いて、α0及び
c!nは上述した固定スクロール及び揺動スクロールで
ある。1211:揺動スクロールωの渦巻体のと反対の
面に設けられた揺動軸、ωは揺動運動の駆動源である電
動機Cl1lにエリ回転する回転駆動軸で、揺動スクロ
ール■と対向する端面で揺動軸I2]+?支承するとと
もに動的バランスを保つバランスウェイト■が固Mされ
ている。vFi吸入口りエリ吸入され7を流体?圧縮す
る圧縮室、lは圧縮さfl、几流体?吐出する吐出口で
ある。−は両スクロールの渦巻体の壁先端面で軸方向の
すき!Thシールするチップシール、ωは揺動スクロー
ルωの自転を防止し、固定スクロールαQと揺動スクロ
ールのとの角度位置を保つオルダム継手、(51)は圧
縮1i1(転)の内圧と揺動スクロール■の自重を支え
る環状のスラスト軸受である。(60)tIi回転回転
駆動軸下部に取り付けられt油ポンプで、各軸受部へ油
供給孔(61)’を通して潤滑油を供給している0この
ように構成され九スクロール流体機械で、電動機罰に給
電するとトルクを発生して回転駆動軸端を回転させる。The above is the operating principle of the scroll fluid machine. Is Figure 5 a conventional scroll fluid machine? It is a diagram showing a basic and refurbished cross-section of the compressor used as a compressor, and FIG. 6 is a diagram showing an enlarged cross-section of its main parts. Both figures Vc's? , α0 and c! n is the above-mentioned fixed scroll and swinging scroll. 1211: An oscillating shaft provided on the opposite side of the spiral body of the oscillating scroll ω, ω is a rotary drive shaft that is rotated by the electric motor Cl1l that is the driving source of the oscillating motion, and is opposed to the oscillating scroll ■. Swing axis I2] +? The balance weight ■ which provides support and maintains dynamic balance is fixed M. vFi inlet is inhaled and 7 is fluid? Compression chamber to be compressed, l is compressed fl, 几fluid? This is a discharge port for discharging. - is the axial clearance at the tip of the wall of the spiral body of both scrolls! Th sealing chip seal, ω is an Oldham joint that prevents the rotation of the oscillating scroll ω and maintains the angular position between the fixed scroll αQ and the oscillating scroll, (51) is the internal pressure of the compression 1i1 (rotation) and the oscillating scroll. ■It is an annular thrust bearing that supports its own weight. (60) An oil pump attached to the lower part of the rotational drive shaft supplies lubricating oil to each bearing part through the oil supply hole (61). When power is supplied to the motor, it generates torque and rotates the end of the rotary drive shaft.
この回転力は揺動軸のに伝達され、揺動スクロール■は
オルダム継手団にガイドされて自転することなく揺動運
動を行い、第4図に示すLうな圧縮作用が行われる。This rotational force is transmitted to the swinging shaft, and the swinging scroll (2) is guided by the Oldham coupling group and performs a swinging motion without rotating on its own axis, and the L-shaped compression action shown in FIG. 4 is performed.
ところで、スクロール流体機械に2いてTfi、信頼性
の面から、液圧縮など圧縮室1内の圧力が異常上昇しt
ときに両渦壱体の壁側面間のすきまを開けて減圧するI
J リーフ機能金持つことが重要である。これに関して
、第5図及び第6図にその基本形を示し友ものでは、揺
動半径を変えられる範囲は軸受のクリアランスのみで決
まるので、殆んどリリーフ機能を持たない。一方、特開
昭59−162383号公報などに記載されているもの
では、揺動半径を可変にして、渦巻体の壁側面間を接触
させるとともにリリーフ機能も持tせている。By the way, in a scroll fluid machine 2, Tfi, from the viewpoint of reliability, if the pressure in the compression chamber 1 increases abnormally due to liquid compression etc.
Sometimes the pressure is reduced by opening a gap between the walls of both vortex bodies.
J It is important to have leaf function money. In this regard, the basic model shown in FIGS. 5 and 6 has almost no relief function because the range in which the swing radius can be changed is determined only by the bearing clearance. On the other hand, in the device described in Japanese Unexamined Patent Publication No. 59-162383, etc., the swing radius is made variable so that the wall surfaces of the spiral body are brought into contact with each other, and a relief function is also provided.
上記の工つな従来のスクロール流体機械では、渦巻体の
壁側面間の接触に伴い振動・騒音や渦巻体壁の摩耗など
の発生要因になるとともに、揺動半径の変化時にそれが
減衰しにくいときには振動騒音が助長されるという課題
があつtoこの発明は、かかる課題を解決するtめにな
され友もので、振動・騒音を少なくしてリリーフ機能金
偏え、信頼性を向上させtスクロール流体機械を得るこ
とを目的とする。In the above-mentioned complicated conventional scroll fluid machines, the contact between the wall surfaces of the spiral body causes vibrations, noise, and wear on the spiral body wall, and it is difficult to attenuate when the oscillation radius changes. Sometimes there is a problem that vibration noise is aggravated, so this invention was made to solve this problem, and it reduces vibration and noise, improves reliability, reduces vibration and noise, and improves the reliability of the scroll fluid. The purpose is to obtain a machine.
この発明に係るスクロール流体機械は、第1の渦巻体を
有する固定スクロールと、片方の面に上記第1の渦巻体
と噛み合わされる第2の渦巻体を、他方の面に揺動軸を
有し揺動運動する揺動スクロールと、この揺動スクロー
ルと対向する端面に、揺動運動のとき偏心する方向と反
対の方向に位置する側面に凹設又は凸設部を有する受?
Il′Jk備えて回転する回転駆動軸と、上記揺動軸を
支承するとともに上記受溝の凹設又は凸設部に嵌合する
6設又は凹設部を有し、上記受道内に摺動自在に配設さ
れて上記回転駆動軸と揺動軸とを連結する揺動軸受体を
備え友ものである。A scroll fluid machine according to the present invention includes a fixed scroll having a first spiral body, a second spiral body meshed with the first spiral body on one surface, and a swing shaft on the other surface. An oscillating scroll that oscillates, and a receiver having a concave or convex portion on the end face opposite to the oscillating scroll, located in a direction opposite to the direction of eccentricity during the oscillating movement.
It has a rotary drive shaft that rotates with Il'Jk, and six grooves or recesses that support the swing shaft and fit into the recesses or protrusions of the receiving groove, and slide into the receiving groove. The present invention includes a swing bearing body which is freely disposed and connects the rotary drive shaft and the swing shaft.
この発明に2いては、揺動軸受体と回転駆動軸端の受溝
との間に設けt凹凸嵌合部で形成される密閉空間が揺動
半径が変化し次ときの振動を緩衝する。In the second aspect of the present invention, the closed space formed by the concave-convex fitting portion provided between the swing bearing body and the receiving groove at the end of the rotary drive shaft changes the swing radius and buffers the next vibration.
第1図はこの発明の一実施例のスクロール流体機械の主
要部を拡大し九縦断面を示す図、第2図は第1図での■
−■部の切断面を示す図であり、図に2いて、cio〜
(61)Fi従来例と同様のものである。(70)/I
i回転駆動軸■の揺動スクロールのと対向する端面に設
けられ友受溝で、揺動運動のとき偏心する方向と反対側
の側面に凹設部(71)を有している。(80)は揺動
軸e2TJ’を支承するとともに受部(70)の凹設部
(71)に嵌合する凸設部(81)’f:有し、受R(
70>内を偏心する方向又はその反対の方向に摺動目在
に配設ざrして回転駆動軸■と揺動軸1211とを連結
する揺動軸受体である。(85)は偏心する方向の受f
i (70)の側面と揺動軸受体(8o)との間に介在
させ°C1尚巻体の壁側面間の接触を避けるときなどに
空隙調整を行うスペーサなどの介在部材である。(91
)は回転駆動軸ω内の油供給孔(61)を経て給油され
る潤滑油を各々の軸受部や受11 (70>に設けられ
之凹設部(71)に゛まで流入させる給油孔、(92)
は給油孔(91)の端部を閉鎖するねじである。FIG. 1 is an enlarged view showing nine longitudinal sections of the main parts of a scroll fluid machine according to an embodiment of the present invention, and FIG.
-It is a diagram showing a cross section of part ■, and in the figure 2, cio~
(61) Fi This is similar to the conventional example. (70)/I
It is a companion groove provided on the end face of the i-rotational drive shaft (2) facing the rocking scroll, and has a recessed portion (71) on the side face opposite to the direction of eccentricity during rocking motion. (80) supports the swing shaft e2TJ' and has a convex part (81)'f: that fits into the recessed part (71) of the receiving part (70), and the receiving part R(
This is a swing bearing body that connects the rotary drive shaft 1 and the swing shaft 1211 by disposing it in a sliding groove in the direction in which the inside of the shaft 70 is eccentric or in the opposite direction. (85) is the receiving f in the eccentric direction
This is an intervening member such as a spacer that is interposed between the side surface of the i (70) and the swing bearing body (8o) to adjust the gap when avoiding contact between the wall surfaces of the roll body. (91
) is an oil supply hole that allows lubricating oil supplied through the oil supply hole (61) in the rotational drive shaft ω to flow into the recessed portion (71) provided in each bearing portion or receiver 11 (70>); (92)
is a screw that closes the end of the oil supply hole (91).
上記のエリに構成され九スクロール流体機櫨に2いて、
まず最初に、液圧縮など圧縮N荀内の圧力が異常上昇し
九ときに渦巻体の壁側面間のすきま?開けて減圧する+
J I)−7機能について説明するO
一般に、揺動式のスクロール流体機械においては、揺動
スクロールが揺動することにより生ずる遠心力、及び圧
縮室内の流体圧力がその外側との差圧にエリ渦巻壁を押
す力の積分としての流体圧力が、第3図に示すように作
用する。即ち、遠心と
力(Fc )は揺動半径(Rr)敵増す方向に、流体圧
力の径方向成分(Fgr)は揺動半径(Rr )を減ら
す方向に、流体圧力の周方向成分(Fgo )に回転駆
動軸の回転の負荷として働く方向にそれぞれ作用する。It is composed of the above Eri, and there are 2 in the nine-scroll fluid machine,
First of all, when the pressure inside the compressor rises abnormally due to liquid compression, etc., the gap between the walls and sides of the spiral body increases. Open and depressurize +
J I)-7 Explaining the functions O Generally, in an oscillating scroll fluid machine, the centrifugal force generated by the oscillating scroll and the fluid pressure inside the compression chamber are affected by the differential pressure between the outside and the outside. The fluid pressure as an integral of the force pushing on the spiral wall acts as shown in FIG. That is, the centrifugal force (Fc) increases the radius of oscillation (Rr), the radial component of fluid pressure (Fgr) decreases the radius of oscillation (Rr), and the circumferential component of fluid pressure (Fgo) They each act in the direction that acts as a rotational load on the rotational drive shaft.
通常の運転の場合には、流体圧力の径方向成分(f’g
r) J: りも遠心力(Fa)が優る友め、揺動半径
(Rr)が増える方向、即ち、渦や体の壁側面のすきま
が小さくなるように働いている。For normal operation, the radial component of fluid pressure (f'g
r) J: The body has a superior centrifugal force (Fa) and works in the direction in which the radius of oscillation (Rr) increases, that is, the vortex and the gap between the side walls of the body become smaller.
さらに、第1図及びts2図に示す実施例に2いては、
潤滑油が給油孔(cn)t−経て揺動軸受体(8o)の
凸設部(81)の周りの狭9部を流れる。このtめ、揺
動軸受体(80)には、狭9部に2ける圧損に基づく差
圧外だけ揺動半径(Rr) ’r:増やす方向、すなわ
ち、遠心力(Fc)と同じ方向の油圧力(F’o )が
作用する。この油圧力(Fo)Vi−油の流量と狭窄部
の広さとで決まるので、例えは可変速運転する場合、低
速時に遠心力が不足するのを補うLうに設定することも
できる。Furthermore, in Example 2 shown in FIG. 1 and ts2,
Lubricating oil flows through the oil supply hole (cn) t- through the narrow portion around the convex portion (81) of the swing bearing body (8o). The oscillating bearing body (80) has a oscillating radius (Rr) 'r: increasing direction, that is, the same direction as the centrifugal force (Fc). Hydraulic pressure (F'o) acts. Since this hydraulic pressure (Fo) Vi is determined by the oil flow rate and the width of the constriction, for example, when operating at variable speed, it can be set to L to compensate for insufficient centrifugal force at low speeds.
このとき、液圧縮などにより圧縮室−円の圧力が異常に
高くなつ九ときには、流体圧力が増大して流体圧力の径
方向成分(Fgr )が遠心力(Fc)と油圧力(Fo
)とに打ち勝つ工うになる。従って、揺動軸受体(8
0)は内向きに移動して揺動半径(Rr)!減らすので
、f!6巻体壁側面間にすきまができリリーフ機能を果
たすことができる。At this time, when the pressure in the compression chamber becomes abnormally high due to liquid compression, etc., the fluid pressure increases and the radial component (Fgr) of the fluid pressure increases with the centrifugal force (Fc) and the hydraulic pressure (Fo
). Therefore, the swing bearing body (8
0) moves inward to the swing radius (Rr)! Because it reduces f! A gap is created between the side walls of the 6-roll body, and a relief function can be achieved.
次に、振動・騒音、特に揺動半径が変化し几ときの振動
の抑制について説明する。まず、通常運転時に2いては
、渦巻体の!1面間が接触しない範囲で、その径方向の
すきiヶ極小となるような揺動半径に設定することがW
ましい。Next, we will explain how to suppress vibrations and noise, especially vibrations that occur when the swing radius changes. First of all, during normal operation, the spiral body! It is best to set the swing radius so that the radial clearance i is minimized within the range where two surfaces do not contact each other.
Delicious.
この九めに、第1図及び第2図に示す実施例に2いては
、回転駆動軸■の揺動スクロールc2I3Hの端面に設
けられt受部(70)の偏心側の側面と揺動軸受体(a
))との間にスペーサ(85)などを介在させている。Ninthly, in the embodiment 2 shown in FIGS. 1 and 2, the eccentric side surface of the t receiving portion (70) and the oscillating bearing are provided on the end face of the oscillating scroll c2I3H of the rotary drive shaft (3). body (a
)) A spacer (85) or the like is interposed between them.
このスペーサC部)の厚さt−a整することにエリ、す
きまが極小になり揺動半径は一定に保すれる。従って2
両渦巻体Iri北接触で運転されるtめ、振動・騒音が
軽減される。一方、運転中に異物の噛み込みや形状誤差
にLる壁面の接触が起l!を場合あるいは、流体圧力が
上昇しt場合などにj?−ては、揺動軸受体(8o)が
受II (70)内で揺動半径を減らす方向に移動して
リリーフし、このあと速やかに元の位置に戻るように動
作する。このとき、略密閉空間である受II (70)
の凹設部(71)はダンパとして作用し、揺動軸受体(
80)の撮動を抑制する。さらに、第1図のように、給
油孔(91)を経て凹設部(71)に潤滑油を充満させ
て2けば、ダンパ効果を工り増大させることができる。By adjusting the thickness t-a of this spacer (C section), the clearance becomes minimal and the swing radius is kept constant. Therefore 2
Since both spiral bodies are operated with north contact, vibration and noise are reduced. On the other hand, during operation, contact with the wall surface may occur due to foreign matter getting caught or shape errors! Or, if the fluid pressure increases and t, then j? In this case, the swing bearing body (8o) moves in the direction of reducing the swing radius within the receiver II (70) to provide relief, and then quickly returns to its original position. At this time, Uke II (70) is a nearly closed space.
The recessed portion (71) acts as a damper, and the rocking bearing body (
80). Furthermore, as shown in FIG. 1, the damper effect can be increased by filling the recess (71) with lubricating oil through the oil supply hole (91).
上記実施例では、渦巻体の壁側面間のすきまを調整する
のにスペーサ金介在させてこの厚みを変えてい九が、渦
巻体などの工作加工や組立の精度を向上させればスペー
サを介在させなくて調整することもできる〇
〔発明の効果〕
この発明は以上説明し九と29、第1の渦巻体を有する
固定スクロールと1片方の面に上記第1の渦巻体と噛み
合わされる第2の渦巻体を、他方の面に揺動軸を有し揺
動運動する揺動スクロールと、この揺動スクロールと対
向する端面に、揺動運動のとき偏心する方向と反対の方
向に位置する側面に凹設又は凸設部を有する受N&を備
えて回転する回転駆動軸と、上記揺動軸を支承するとと
もに上記受溝の凹設又は凸設部に嵌合する6設又は凹設
部を有し、上記受溝内に摺動自在に配設されて上記回転
駆動軸と揺動軸とを連結する揺動軸受体を備える構成に
し九ので、振動・騒音を少なくしてリリーフ機能が得ら
れ、信頼性を向上できる効果がある。In the above embodiment, a spacer metal is used to adjust the gap between the wall surfaces of the spiral body and the thickness is changed. However, if the accuracy of machining and assembly of the spiral body is improved, a spacer can be inserted. 〇 [Effects of the Invention] This invention has been explained above. An oscillating scroll that has a oscillating shaft on the other surface and that oscillates, and a side surface that is located in the opposite direction to the direction of eccentricity during the oscillating movement, on the end surface facing the oscillating scroll. A rotary drive shaft that rotates with a receiver N & having a concave or convex portion on the receiving groove; and a rocking bearing body that is slidably disposed in the receiving groove and connects the rotary drive shaft and the rocking shaft, thereby reducing vibration and noise and providing a relief function. This has the effect of improving reliability.
第1図はこの発明の一実施例のスクロール流体機械の主
要部を拡大し次縦断面金示す図、第2図は第1図の実施
例での一切断面を示す図、第3図は揺動スクロールに作
用する力の関係を示す説明図、第4図はスクローA/f
11.体機械の動作原理図、第5図は従来のスクロール
流体機械全体の縦断面を示す図、第6図は第5図の主要
部の拡大断面を示す図である。
図において、0.0は固定スクロール、■は揺動スクロ
ール、QJJは揺動軸、(3+)は回転駆動軸、 (
70)は受溝、(80)IIi揺動軸受体である。
12、各図中、同一符号は同一、ま之は相当部分を示す
。FIG. 1 is an enlarged longitudinal cross-sectional view of the main parts of a scroll fluid machine according to an embodiment of the present invention, FIG. 2 is a diagram showing a complete cross-section of the embodiment of FIG. 1, and FIG. An explanatory diagram showing the relationship of forces acting on the moving scroll, Fig. 4 is the scroll A/f
11. FIG. 5 is a diagram showing the longitudinal cross section of the entire conventional scroll fluid machine, and FIG. 6 is a diagram showing an enlarged cross section of the main part of FIG. 5. In the figure, 0.0 is a fixed scroll, ■ is an oscillating scroll, QJJ is an oscillating axis, (3+) is a rotating drive axis, (
70) is a receiving groove, and (80) IIi is a swing bearing body. 12. In each figure, the same reference numerals indicate the same parts, and the numbers indicate corresponding parts.
Claims (1)
記第1の渦巻体と噛み合わされる第2の渦巻体を、他方
の面に揺動軸を有し揺動運動する揺動スクロール、この
揺動スクロールと対向する端面に、揺動運動のとき偏心
する方向と反対の方向に位置する側面に凹設又は凸設部
を有する受溝を備えて回転する回転駆動軸、及び前記揺
動軸を支承するとともに前記受溝の凹設又は凸設部に嵌
合する凸設又は凹設部を有し、前記受溝内に摺動自在に
配設されて前記回転駆動軸と前記揺動軸とを連結する揺
動軸受体を備えたことを特徴とするスクロール流体機械
。A fixed scroll having a first spiral body; an oscillating scroll having a second spiral body meshed with the first spiral body on one surface and a rocking shaft on the other surface; A rotary drive shaft that rotates and has a receiving groove having a concave or convex portion on a side surface located in a direction opposite to the direction of eccentricity during the rocking motion, on an end face facing the rocking scroll, and the rocking shaft. and a convex or concave portion that fits into a concave or convex portion of the receiving groove, and is slidably disposed within the receiving groove and supports the rotary drive shaft and the swing shaft. A scroll fluid machine characterized by comprising a swing bearing body that connects the scroll fluid machine.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP19689688A JPH0245672A (en) | 1988-08-06 | 1988-08-06 | Scroll fluid machine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP19689688A JPH0245672A (en) | 1988-08-06 | 1988-08-06 | Scroll fluid machine |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH0245672A true JPH0245672A (en) | 1990-02-15 |
Family
ID=16365454
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP19689688A Pending JPH0245672A (en) | 1988-08-06 | 1988-08-06 | Scroll fluid machine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0245672A (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0450489A (en) * | 1990-06-20 | 1992-02-19 | Mitsubishi Electric Corp | Scroll compressor |
JPH04191489A (en) * | 1990-11-26 | 1992-07-09 | Mitsubishi Electric Corp | Scroll compressor |
EP0498163A1 (en) * | 1991-02-04 | 1992-08-12 | Tecumseh Products Company | Scroll compressor |
US5165879A (en) * | 1990-08-30 | 1992-11-24 | Mitsubishi Jukogyo Kabushiki Kaisha | Scroll type fluid machinery with driving pin in bushing slide groove |
US5520527A (en) * | 1993-12-30 | 1996-05-28 | Goldstar Co., Ltd. | Apparatus for adjusting orbital radius in a scroll compressor |
WO1999015764A1 (en) * | 1997-09-22 | 1999-04-01 | Mind Tech Corp. | Scroll-type fluid displacement device having flow diverter, multiple tip seal and semi-radial compliant mechanism |
US6193487B1 (en) | 1998-10-13 | 2001-02-27 | Mind Tech Corporation | Scroll-type fluid displacement device for vacuum pump application |
-
1988
- 1988-08-06 JP JP19689688A patent/JPH0245672A/en active Pending
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0450489A (en) * | 1990-06-20 | 1992-02-19 | Mitsubishi Electric Corp | Scroll compressor |
US5165879A (en) * | 1990-08-30 | 1992-11-24 | Mitsubishi Jukogyo Kabushiki Kaisha | Scroll type fluid machinery with driving pin in bushing slide groove |
AU639566B2 (en) * | 1990-08-30 | 1993-07-29 | Mitsubishi Jukogyo Kabushiki Kaisha | Scroll type fluid machinery |
JPH04191489A (en) * | 1990-11-26 | 1992-07-09 | Mitsubishi Electric Corp | Scroll compressor |
EP0498163A1 (en) * | 1991-02-04 | 1992-08-12 | Tecumseh Products Company | Scroll compressor |
US5520527A (en) * | 1993-12-30 | 1996-05-28 | Goldstar Co., Ltd. | Apparatus for adjusting orbital radius in a scroll compressor |
WO1999015764A1 (en) * | 1997-09-22 | 1999-04-01 | Mind Tech Corp. | Scroll-type fluid displacement device having flow diverter, multiple tip seal and semi-radial compliant mechanism |
US6071101A (en) * | 1997-09-22 | 2000-06-06 | Mind Tech Corp. | Scroll-type fluid displacement device having flow diverter, multiple tip seal and semi-radial compliant mechanism |
US6193487B1 (en) | 1998-10-13 | 2001-02-27 | Mind Tech Corporation | Scroll-type fluid displacement device for vacuum pump application |
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