JPS61215480A - Scroll type compressor - Google Patents

Scroll type compressor

Info

Publication number
JPS61215480A
JPS61215480A JP60056843A JP5684385A JPS61215480A JP S61215480 A JPS61215480 A JP S61215480A JP 60056843 A JP60056843 A JP 60056843A JP 5684385 A JP5684385 A JP 5684385A JP S61215480 A JPS61215480 A JP S61215480A
Authority
JP
Japan
Prior art keywords
orbiting scroll
scroll
shaft
eccentric
rollers
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
Application number
JP60056843A
Other languages
Japanese (ja)
Other versions
JPH0551073B2 (en
Inventor
Takao Yoshimura
多佳雄 吉村
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Holdings Corp
Original Assignee
Matsushita Refrigeration Co
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Matsushita Refrigeration Co filed Critical Matsushita Refrigeration Co
Priority to JP60056843A priority Critical patent/JPS61215480A/en
Publication of JPS61215480A publication Critical patent/JPS61215480A/en
Publication of JPH0551073B2 publication Critical patent/JPH0551073B2/ja
Granted legal-status Critical Current

Links

Classifications

    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/50—Other types of ball or roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/10—Bearings, parts of which are eccentrically adjustable with respect to each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/42—Pumps with cylinders or pistons

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

PURPOSE:To reduce incurrence of a friction loss between a boss part and a projection, by a method wherein an eccentric roller bearing, formed with a holding device and plural rollers different in size, is secured to the boss part of a shaft, and the projection of a turning scroll is inserted in the bearing. CONSTITUTION:An eccentric roller bearing 19 is formed with cylindrical rollers 20a-22h different in size and a holding device 21. In this case, the rollers 20a-20h are held by the holding device 21 so that a relative position therebetween is prevented from a change, and are brought into rotatable contact with the holding device 21. The holding device 21 is pressed in a boss part 11a of a shaft 11 for securing, and a projection 10 of a swirl scroll is inserted internally of the inner diameter side of an eccentric roller 19. This an outer size center O0 and an inner size center O4 of the eccentric roller 19 is eccentrically deviated by a constant amount E2. This causes the projection 10 of the swirl scroll and the boss part 11a of the shaft 11 to be slid over each other through the rollers 20a-20h, resulting decrease of incurring of a friction loss.

Description

【発明の詳細な説明】 産業上の利用分野 本発明は冷凍サイクル等に使用するスクロール型圧縮機
に関し、特に体積効率が良好で且つ機械損失の少ない軸
受構造に係わる。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a scroll compressor used in a refrigeration cycle or the like, and particularly relates to a bearing structure with good volumetric efficiency and low mechanical loss.

従来の技術 従来の構成を第４図、第６図、第６図にて説明する。Conventional technology The conventional configuration will be explained with reference to FIGS. 4, 6, and 6.

１は密閉ケーシング、２は電動機部であり、その上部に
はブロック３．固定スクロール４．旋回スクロール６、
自転防止機構６にて構成される機械部本体７が固定され
ている。固定スクロール４は、鏡板４＆及び鏡板４ａに
直立するインボリュート又はインボリュートに類似した
曲線の一様な厚さを有するジップ４ｂより構成され、鏡
板４ａにてブロック３に固定されている。又、旋回スク
ロール６は鏡板５ａ及び鏡板６ａに直立し、固定スクロ
ール４０ラツプ４ｂと同じ曲線を有するラップ６ｂより
構成され、鏡板６ａは、固定スクロール４の鏡板４ａと
ブロック３にクリアランスＡを設けてはさみ込み支持さ
れ、かつ自転防止機構６により拘束されている。そして
、固定スクロール４と旋回スクロール６は、各ラップａ
ｂ　、　ｓｂの巻き終り端４ｂ’、ｅｓｂ’をある角度
ずらした状態で合わされている。1 is a sealed casing, 2 is an electric motor section, and a block 3. Fixed scroll 4. orbiting scroll 6,
A mechanical part main body 7 constituted by an anti-rotation mechanism 6 is fixed. The fixed scroll 4 is composed of an end plate 4& and a zip 4b having a uniform thickness and an involute or an involute-like curve standing upright on the end plate 4a, and is fixed to the block 3 by the end plate 4a. The orbiting scroll 6 is composed of an end plate 5a and a wrap 6b that stands upright on the end plate 6a and has the same curve as the fixed scroll 40 wrap 4b, and the end plate 6a has a clearance A between the end plate 4a of the fixed scroll 4 and the block 3. It is sandwiched and supported, and is restrained by an anti-rotation mechanism 6. The fixed scroll 4 and the orbiting scroll 6 each have a
The end ends 4b' and esb' of windings b and sb are shifted by a certain angle and put together.

８は吐出孔、９は吸入孔であり、吐出孔８は固定スクロ
ール４のインボリュートの中心部に、又吸入孔９は固定
スクロール４のインボリュートの鏡板４ａの外縁部に設
けられている。１０は、旋回スクロール６のラップ６ｂ
と反対側の面に設けられた突起であシ、ラップ６ｂのイ
ンボリュートの中心と同心である。１１はブロック３に
スラスト軸受１２を介して支承されたシャフトであり、
機械部本体７の端部に設けられたシャフト中／岬。8 is a discharge hole, and 9 is a suction hole. The discharge hole 8 is provided at the center of the involute of the fixed scroll 4, and the suction hole 9 is provided at the outer edge of the end plate 4a of the involute of the fixed scroll 4. 10 is a wrap 6b of the orbiting scroll 6
The protrusion provided on the opposite surface is concentric with the center of the involute of the wrap 6b. 11 is a shaft supported by the block 3 via a thrust bearing 12;
A shaft middle/cape provided at the end of the mechanical part main body 7.

より一定量Ｅ２偏心したボス部１１　ａＫ偏心ブツシュ
１３を収納している。偏心ブツシュ１３は、外径中心ｏ
２よりある一定量Ｅ２偏心した位置に中心０３のある偏
心穴１３ａを有し外径中心０２を中心としてボス部り１
ａ内を自由に回転できる。A boss portion 11 aK which is eccentric by a certain amount E2 accommodates an eccentric bush 13. The eccentric bushing 13 has an outer diameter center o
2, there is an eccentric hole 13a with a center 03 at a position that is eccentric by a certain amount E2 from 2, and a boss portion 1 with the outer diameter center 02 as the center.
It can rotate freely within a.

また偏心穴１３ａｌｔｃは旋回スクロール６の突起１ｏ
を収納し、電動機部２と旋回スクロール６を連結してい
る。また、シャフト１１の中心部には給油孔１１ｂが貫
通しておシ、シャフト１１のボス部１１ａと旋回スクロ
ール６の突起１０により形成される油溜め空間１４と密
閉ケーシング１の下部を連通している。１５は旋回スク
ロール５の背面に形成された背圧室であシ、旋回スクロ
ール６０ラツプ６ｂ側とは鏡板５ａ、４ａ部のクリアラ
ンスＡより低圧部と連通している。１６は吸入孔９と連
通する吸入管、１７は吐出管である。また、１８は密閉
ケーシング１の下部に溜った潤滑油である。Moreover, the eccentric hole 13altc is the projection 1o of the orbiting scroll 6.
The electric motor section 2 and the orbiting scroll 6 are connected to each other. Further, an oil supply hole 11b passes through the center of the shaft 11, and communicates the oil reservoir space 14 formed by the boss portion 11a of the shaft 11 and the protrusion 10 of the orbiting scroll 6 with the lower part of the sealed casing 1. There is. Reference numeral 15 designates a back pressure chamber formed on the back surface of the orbiting scroll 5, and the wrap 6b side of the orbiting scroll 60 communicates with a lower pressure section than the clearance A between the end plates 5a and 4a. 16 is a suction pipe communicating with the suction hole 9, and 17 is a discharge pipe. Moreover, 18 is lubricating oil accumulated in the lower part of the sealed casing 1.

次にスクロール圧縮機の圧縮機構について説明する。電
動機部２０回転に伴うシャフト１１０回転運動は、ボス
部１１ａ、偏心ブツシュ１３．突起１０を介して旋回ス
クロール６に伝達されるが、自転防止機構６の作用によ
り旋回スクロール６は自転することなく固定スクロール
４のインボリュートの中心を旋回中心として旋回運動す
る。このとき、旋回スクロール６のラップ６ｂの巻き終
り端ｓ　ｂ’が固定スクロール４のラップ４ｂに、固定
スクロール４０ラツプ４ｂの巻き終り端４ｂ’が旋回ス
クロール６０ラツプ６ｂに各々接触している状態が吸入
完了であり、旋回スクロール６の公転運動に伴いラップ
４ｂとラップ５ｂ同士の２つの接触点がインボリュート
の中心に近づくに従い圧縮空間Ｓの圧力が上昇する。Next, the compression mechanism of the scroll compressor will be explained. The rotational movement of the shaft 110 accompanying the rotation of the electric motor section 20 is caused by the rotation of the boss section 11a, the eccentric bushing 13. The signal is transmitted to the orbiting scroll 6 via the protrusion 10, but due to the action of the rotation prevention mechanism 6, the orbiting scroll 6 rotates around the involute center of the fixed scroll 4 without rotating on its own axis. At this time, the end sb' of the wrap 6b of the orbiting scroll 6 is in contact with the wrap 4b of the fixed scroll 4, and the end 4b' of the wrap 4b of the fixed scroll 40 is in contact with the wrap 6b of the orbiting scroll 60. Inhalation is complete, and the pressure in the compression space S increases as the two contact points between the wraps 4b and 5b approach the center of the involute as the orbiting scroll 6 revolves.

このスクロール圧縮機の圧縮機構により、吸入管１６よ
り吸入孔９を介して吸入された冷媒は圧縮され吐出孔８
を介して一旦密閉ケーシング１内に吐出された後、吐出
管１７を介して冷却システム（図示せず）に吐出される
。By the compression mechanism of this scroll compressor, the refrigerant sucked from the suction pipe 16 through the suction hole 9 is compressed and the refrigerant is compressed through the discharge hole 8.
After being once discharged into the closed casing 1 through the discharge pipe 17, it is discharged into a cooling system (not shown).

この圧縮の行程において、偏心ブツシュ１３には旋回ス
クロール６の突起１ｏを介して圧縮負荷と旋回スクロー
ル６の遠心力の合力Ｆが作用する。During this compression stroke, a resultant force F of the compression load and the centrifugal force of the orbiting scroll 6 acts on the eccentric bush 13 via the projection 1o of the orbiting scroll 6.

この力Ｆは、偏心プッシユ１３の中心０□と偏心穴１３
ａの中心０３を結ぶ直線に直角な分力Ｆ′を発生し、更
に偏心ブツシュ１１はボス部り１ａ内を自由に回転でき
る様に構成されている為、旋回スクロール６の突起１ｏ
は中心ｏ２のまわりに回転させられ様とし、シャフト中
心ｏ１　　と旋回スクロール６の突起１ｏの中心０２の
間の旋回半径Ｒは増大しようとする。この結果、旋回ス
クロール６０ラフグ６ｂと固定スクロール４のラップ４
ｂは接触し半径方向のクリアランスが０となる為、圧縮
室からの漏れが減少し体積効率が向上するようになって
いる。例えば米国特許第１９０６１４２号明細書、特開
昭５８−９６１９３号公報、特開昭５９−１６２３８３
号公報である。This force F is between the center 0□ of the eccentric pusher 13 and the eccentric hole 13.
generates a component force F' perpendicular to the straight line connecting the center 03 of
is likely to be rotated around the center o2, and the turning radius R between the shaft center o1 and the center 02 of the protrusion 1o of the orbiting scroll 6 is likely to increase. As a result, the orbiting scroll 60 luff 6b and the wrap 4 of the fixed scroll 4
b are in contact and the radial clearance becomes 0, so leakage from the compression chamber is reduced and volumetric efficiency is improved. For example, U.S. Pat.
This is the publication number.

発明が解決しようとする問題点 このような従来の方法では、確かに体積効率の向上は図
れるが、旋回スクロールの突起と偏心ブツシュの偏心大
間はすべり接触であり、摩擦損失が多い問題があった。Problems to be Solved by the Invention Although it is true that volumetric efficiency can be improved with such conventional methods, there is a sliding contact between the protrusions of the orbiting scroll and the eccentric diameter of the eccentric bushing, which causes a problem of high friction loss. .

これに対して、偏心ブツシュの偏心穴に摩擦損失の少な
いコロ軸受を圧入する方法も考えられるが、偏心ブツシ
ュ及びシャフトボス部が大径化する問題があった。A possible solution to this problem is to press-fit a roller bearing with low friction loss into the eccentric hole of the eccentric bushing, but this has the problem of increasing the diameter of the eccentric bushing and shaft boss.

本発明は上記従来例の欠点を解消するもので、旋回半径
を可変とし運転中での旋回スクロールと固定スクロール
のラップ間の半径方向のクリアランスをゼロとし、漏れ
による体積効率の低下を防止し、また旋回スクロールと
シャフトの連結部分での摩擦損失を低減し性能の向上を
図ることを目的としている。The present invention solves the above-mentioned drawbacks of the conventional example, and makes the radius of revolution variable so that the radial clearance between the laps of the orbiting scroll and the fixed scroll during operation is zero, thereby preventing a decrease in volumetric efficiency due to leakage. It also aims to improve performance by reducing friction loss at the connection between the orbiting scroll and the shaft.

問題点を解決するだめの手段 本発明は、従来のすべり軸受として作用する偏心ブツシ
ュに代えて、保持器と直径の異なる複数個のコロより形
成され且つコロの相対位置が変化しない様に保持器に接
触回動する偏心コロ軸受をシャフトのボス部に固定する
と共に旋回スクロールの突起を内挿したものである。Means for Solving the Problems The present invention replaces the conventional eccentric bushing that acts as a sliding bearing with a retainer that is formed of a plurality of rollers with different diameters and that is configured such that the relative position of the rollers does not change. An eccentric roller bearing that rotates in contact with the shaft is fixed to the boss portion of the shaft, and the protrusion of the orbiting scroll is inserted therein.

作　　用 本発明は上記した構成により、従来と同様に、圧縮負荷
と遠心力が作用すると旋回スクロールは偏心コロ軸受の
中心のまわりに回転させられ様とし、この結果旋回スク
ロールと固定スクロールのラップが接触し半径方向のク
リアランスがゼロとなる為、圧縮室からの漏れが減少し
体積効率が向上すると共に、旋回スクロールの突起とシ
ャフトのボス部間にコロ軸受が介在することとなり、摩
擦損失も減少し性能指数が向上する。Effect of the present invention With the above-described configuration, the orbiting scroll tends to rotate around the center of the eccentric roller bearing when compressive load and centrifugal force act, as in the conventional case, and as a result, the lap between the orbiting scroll and the fixed scroll is caused to rotate. Since they are in contact and the radial clearance is zero, leakage from the compression chamber is reduced and volumetric efficiency is improved, and since a roller bearing is interposed between the protrusion of the orbiting scroll and the boss of the shaft, friction loss is also reduced. performance index is improved.

実施例 以下本発明の一実施例を第１図、第２図及び第３図にて
説明する。EXAMPLE An example of the present invention will be described below with reference to FIGS. 1, 2, and 3.

尚、従来例と同一部分は同一符号を付し説明を省略する
。１９は２０ａ　、　２ｏｂ　、　２ｏｃ、２ｏｄ。Incidentally, the same parts as in the conventional example are given the same reference numerals, and the description thereof will be omitted. 19 is 20a, 2ob, 2oc, 2od.

２０ｓ　、２０　ｆ　、２０ｇ　、２０ｈの直径の異な
る円筒状のコロと保持器２１により構成される偏心コロ
軸受である。またコロ２０ａ〜２ｏｈは保持器２１によ
りその相対位置が変化しない様に保持されると共に保持
器２１に接触回動する。保持器２１はシャフト１１のボ
ス部１１ａに圧入固定され、更に偏心コロ軸受１９の内
径側には旋回スクロール５の突起１ｏが内挿されている
。この結果、偏心コロ軸受１９の外径中心ｏ６と内径中
心ｏ４は、従来と同様に一定量Ｅ２偏心している仁とと
なる。This is an eccentric roller bearing composed of cylindrical rollers with different diameters of 20s, 20f, 20g, and 20h and a retainer 21. Further, the rollers 20a to 2oh are held by the cage 21 so that their relative positions do not change, and are rotated in contact with the cage 21. The cage 21 is press-fitted into the boss portion 11a of the shaft 11, and the protrusion 1o of the orbiting scroll 5 is inserted into the inner diameter side of the eccentric roller bearing 19. As a result, the outer diameter center o6 and the inner diameter center o4 of the eccentric roller bearing 19 become eccentric by a certain amount E2 as in the conventional case.

圧縮の行程において、偏心コロ軸受１９には圧縮負荷と
旋回スクロール６の遠心力の合力Ｆが従来と同様作用し
、偏心コロ軸受１９の外学中心ｏ６と内径中心０４を結
ぶ直線に直角な分力Ｆ′　を発生する。偏心コロ軸受１
９は、コロ２０　ａ〜２０ｈがその相対位置を変化する
ことなく外径中心ｏ６のまわりに自由忙回転する様に構
成されている為に、旋回スクロール６の突起１ｏは中心
ｏ６のまわシに回転させられ様とし、シャフト中心ｏ１
　と旋回スクロール６の突起１ｏの中心０４間の旋回半
径Ｒは増大しようとする。この結果、従来と同様に旋回
スクロール６のラップ６ｂと固定スクロール４０ラツプ
４ｂは、接触し半径方向のクリアランスがゼロとなる為
に圧縮室からの漏れが減少し体積効率が向上する。During the compression stroke, the resultant force F of the compression load and the centrifugal force of the orbiting scroll 6 acts on the eccentric roller bearing 19 in the same manner as before, and the force F acting on the eccentric roller bearing 19 perpendicular to the straight line connecting the external center o6 and the internal center 04 of the eccentric roller bearing 19 acts on the eccentric roller bearing 19. A force F' is generated. Eccentric roller bearing 1
9 is configured such that the rollers 20a to 20h rotate freely around the outer diameter center o6 without changing their relative positions, so the protrusion 1o of the orbiting scroll 6 rotates around the center o6. As if it were rotated, the shaft center o1
and the center 04 of the protrusion 1o of the orbiting scroll 6 tends to increase. As a result, the wrap 6b of the orbiting scroll 6 and the wrap 4b of the fixed scroll 40 come into contact with each other and the radial clearance becomes zero, as in the conventional case, so that leakage from the compression chamber is reduced and volumetric efficiency is improved.

又、従来に加えて、旋回スクロール６の突起１０とシャ
フト１１のボス部１１ａ間の摺動がコロ２０ａ〜２ｏｈ
を介して行なわれることとなり、摩擦損失が減少し入力
が低減される為、性能指数が向上し、更に、従来の偏心
ブツシュ弐にコロ軸受を組合せる方式に比べて小型化を
図れる。In addition to the conventional method, the sliding movement between the protrusion 10 of the orbiting scroll 6 and the boss portion 11a of the shaft 11 is caused by rollers 20a to 2oh.
Since friction loss and input are reduced, the performance index is improved, and furthermore, the size can be reduced compared to the conventional method of combining roller bearings with eccentric bushes 2.

発明の効果 以上の説明から明らかな様に本発明は、互いにる自転防
止機構と、一端に偏心したボス部を有するシャフトと、
旋回スクロールのラップと鏡板を介して反対側に設けら
れた突起と、直径の異なる複数個のコロとコロの相対位
置が変化しないように保持し且つコロが接触回動する保
持器より形成され、この保持器の外径中心とカロにより
形成される内径中心が偏心した偏心コロ軸受を備え、保
持器をボス部に固定すると共に、旋回スクロール回スク
ロールは偏心コロ軸受のまわりに回転させられ様とし、
この結果旋回スクロールと固定スクロールのラップが接
触し半径方向のり・リアランスがゼロとなる為、圧縮室
からの漏れが減少し体積効率が向上すると共に、旋回ス
クロールの突起とシャフトのボス部間に摩擦係数の小さ
いコロ軸受が介在することとなり摩擦損失も減少し、更
に偏心ブツシュとコロ軸受を併用する場合に比べて小型
化を図ることができる。Effects of the Invention As is clear from the above description, the present invention has two mutual rotation prevention mechanisms, a shaft having an eccentric boss portion at one end,
It is formed of a protrusion provided on the opposite side of the orbiting scroll through the lap and end plate, a plurality of rollers having different diameters, and a retainer that holds the rollers so that their relative positions do not change and that the rollers rotate in contact with each other, The cage is equipped with an eccentric roller bearing whose inner diameter center formed by the center of the outer diameter is eccentric, and the cage is fixed to the boss part, and the orbiting scroll is rotated around the eccentric roller bearing. ,
As a result, the wraps of the orbiting scroll and the fixed scroll come into contact and radial glide and rearance become zero, reducing leakage from the compression chamber and improving volumetric efficiency, as well as friction between the protrusions of the orbiting scroll and the boss of the shaft. Since a roller bearing with a small coefficient is interposed, friction loss is also reduced, and furthermore, it is possible to achieve a reduction in size compared to the case where an eccentric bush and a roller bearing are used together.

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

第１図は本発明の一実施例を示すスクロール型圧縮機の
偏心コロ軸受の拡大断面図、第２図は第１図のｕ　−ｎ
’　　線における断面図、第３図は同第１図のスクロー
ル型圧縮機の縦断面図、第４図は従来のスクロール型圧
縮機を示す縦断面図、第６図は第４図のｖ　−ｖ’　線
における断面図、第６因は従来の偏心ブツシュの拡大断
面図である。 ４・・・・・・ＩＩ定Ｘ／ロール、４ａ・・・・・・固
定スクロールの鏡板、４ｂ・・・・・・固定スクロール
のラップ、６・・・・・・旋回スクロール、６ａ・・・
・・・旋回スクロールの鏡板、６ｂ・・・・・・旋回ス
クロールのラップ、６・・・・・・自転防止機構、１０
・・・・・・旋回スクロールの突起部、１１・・・・・
・シャフト、１１ａ・・・・・・シャフトのボス部、１
９・・・・・・偏心コロ軸受、２ｏａ〜２０ｈ・・・・
・・＝１０．２１・・・・・・保持器。 代理人の氏名　弁理士　中　尾　敏　男　ほか１名５・
１．４定、＠ス２トル に・・・４趣回ヌクυ−九ノリ（起 ／ｌ・・・　シャフト ／ＩＱ・・・シャフトめボ２虐６ ２１　・・・　イ、ｙｎ　　メ ５・・・掟回ヌ２トル ＩＩ・・・ＶｖｙトFIG. 1 is an enlarged sectional view of an eccentric roller bearing of a scroll compressor showing an embodiment of the present invention, and FIG.
3 is a vertical sectional view of the scroll compressor shown in FIG. 1, FIG. 4 is a vertical sectional view of a conventional scroll compressor, and FIG. The sectional view taken along line v', the sixth factor, is an enlarged sectional view of a conventional eccentric bushing. 4...II constant X/roll, 4a...Fixed scroll end plate, 4b...Fixed scroll wrap, 6...Orbiting scroll, 6a...・
...End plate of the orbiting scroll, 6b...Wrap of the orbiting scroll, 6...Rotation prevention mechanism, 10
...Protrusion of the orbiting scroll, 11...
・Shaft, 11a...Shaft boss part, 1
9...Eccentric roller bearing, 2oa~20h...
...=10.21...Cage. Name of agent: Patent attorney Toshio Nakao and 1 other person5.
1.4 constant, @su2tor...4 times nuku υ-9 nori (start/l...shaft/IQ...shaft mebo 2 torture 6 21... I, yn me5...・・Rule times 2 toru II・・Vvyto

Claims (1)

【特許請求の範囲】[Claims] 互いにかみ合うラップを鏡板より直立させた固定及び旋
回スクロールと、前記旋回スクロールの自転を防止し旋
回運動を行なわせる自転防止機構と、一端に偏心したボ
ス部を有するシャフトと、前記旋回スクロールのラップ
と鏡板を介して反対側に設けられた突起と、直径の異な
る複数個の円筒状のコロと前記コロ間の相対位置が変化
しない様に保持し且つ前記コロが接触回動する保持器よ
り形成される偏心コロ軸受とを備え、前記保持器を前記
ボス部に固定すると共に、前記旋回スクロールの突起を
偏心コロ軸受へ内挿したスクロール型圧縮機。A fixed and orbiting scroll having interlocking wraps standing upright from an end plate, an anti-rotation mechanism that prevents rotation of the orbiting scroll and allows the orbiting movement to occur, a shaft having an eccentric boss portion at one end, and a wrap of the orbiting scroll. It is formed of a protrusion provided on the opposite side with an end plate interposed therebetween, a plurality of cylindrical rollers having different diameters, and a retainer that holds the rollers so that their relative positions do not change and that the rollers rotate in contact with each other. What is claimed is: 1. A scroll type compressor comprising: an eccentric roller bearing; the retainer is fixed to the boss portion; and a protrusion of the orbiting scroll is inserted into the eccentric roller bearing.
JP60056843A 1985-03-20 1985-03-20 Scroll type compressor Granted JPS61215480A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP60056843A JPS61215480A (en) 1985-03-20 1985-03-20 Scroll type compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP60056843A JPS61215480A (en) 1985-03-20 1985-03-20 Scroll type compressor

Publications (2)

Publication Number Publication Date
JPS61215480A true JPS61215480A (en) 1986-09-25
JPH0551073B2 JPH0551073B2 (en) 1993-07-30

Family

ID=13038686

Family Applications (1)

Application Number Title Priority Date Filing Date
JP60056843A Granted JPS61215480A (en) 1985-03-20 1985-03-20 Scroll type compressor

Country Status (1)

Country Link
JP (1) JPS61215480A (en)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63159689A (en) * 1986-12-23 1988-07-02 Sanyo Electric Co Ltd Scroll compressor
JPH02168016A (en) * 1988-10-06 1990-06-28 Carrier Corp Bearing device and scroll compressor
US5104302A (en) * 1991-02-04 1992-04-14 Tecumseh Products Company Scroll compressor including drive pin and roller assembly having sliding wedge member
WO2011138075A1 (en) * 2010-05-05 2011-11-10 Robert Bosch Gmbh Eccentric bearing
WO2011138078A1 (en) * 2010-05-05 2011-11-10 Robert Bosch Gmbh Eccentric bearing
WO2011138076A1 (en) * 2010-05-05 2011-11-10 Robert Bosch Gmbh Eccentric bearing
US20120036996A1 (en) * 2010-08-12 2012-02-16 Robert Bosch Gmbh Piston Pumps for a Hydraulic Vehicle Brake System
CN102884327A (en) * 2010-05-05 2013-01-16 罗伯特·博世有限公司 Eccentric bearing
JP2022529551A (en) * 2019-04-23 2022-06-23 ザ・ティムケン・カンパニー Roll ordering to improve bearing runout

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63159689A (en) * 1986-12-23 1988-07-02 Sanyo Electric Co Ltd Scroll compressor
JPH02168016A (en) * 1988-10-06 1990-06-28 Carrier Corp Bearing device and scroll compressor
US5111712A (en) * 1988-10-06 1992-05-12 Carrier Corporation Rolling element radial compliancy mechanism
US5104302A (en) * 1991-02-04 1992-04-14 Tecumseh Products Company Scroll compressor including drive pin and roller assembly having sliding wedge member
CN102893041A (en) * 2010-05-05 2013-01-23 罗伯特·博世有限公司 Eccentric bearing
JP2013531191A (en) * 2010-05-05 2013-08-01 ロベルト・ボッシュ・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング Eccentric bearing
WO2011138076A1 (en) * 2010-05-05 2011-11-10 Robert Bosch Gmbh Eccentric bearing
US9506541B2 (en) 2010-05-05 2016-11-29 Robert Bosch Gmbh Eccentric bearing
CN102884328A (en) * 2010-05-05 2013-01-16 罗伯特·博世有限公司 Eccentric bearing
CN102884327A (en) * 2010-05-05 2013-01-16 罗伯特·博世有限公司 Eccentric bearing
WO2011138075A1 (en) * 2010-05-05 2011-11-10 Robert Bosch Gmbh Eccentric bearing
JP2013525710A (en) * 2010-05-05 2013-06-20 ロベルト・ボッシュ・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング Eccentric bearing
JP2013525711A (en) * 2010-05-05 2013-06-20 ロベルト・ボッシュ・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング Eccentric bearing
WO2011138078A1 (en) * 2010-05-05 2011-11-10 Robert Bosch Gmbh Eccentric bearing
US20130195390A1 (en) * 2010-05-05 2013-08-01 Robert Bosch Gmbh Eccentric Bearing
JP2013533436A (en) * 2010-05-05 2013-08-22 ロベルト・ボッシュ・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング Eccentric bearing
US8870463B2 (en) 2010-05-05 2014-10-28 Robert Bosch Gmbh Eccentric bearing
US8950942B2 (en) * 2010-05-05 2015-02-10 Robert Bosch Gmbh Eccentric bearing
CN102893041B (en) * 2010-05-05 2015-11-25 罗伯特·博世有限公司 Capacity eccentric bearing
US20120036996A1 (en) * 2010-08-12 2012-02-16 Robert Bosch Gmbh Piston Pumps for a Hydraulic Vehicle Brake System
JP2022529551A (en) * 2019-04-23 2022-06-23 ザ・ティムケン・カンパニー Roll ordering to improve bearing runout
US11767880B2 (en) 2019-04-23 2023-09-26 The Timken Company Roller sequencing for improved bearing runout

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