JP2572215B2 - Crankshaft structure of scroll compressor - Google Patents
Crankshaft structure of scroll compressorInfo
- Publication number
- JP2572215B2 JP2572215B2 JP22958286A JP22958286A JP2572215B2 JP 2572215 B2 JP2572215 B2 JP 2572215B2 JP 22958286 A JP22958286 A JP 22958286A JP 22958286 A JP22958286 A JP 22958286A JP 2572215 B2 JP2572215 B2 JP 2572215B2
- Authority
- JP
- Japan
- Prior art keywords
- crankshaft
- main shaft
- bearing
- diameter
- scroll compressor
- 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.)
- Expired - Lifetime
Links
Landscapes
- Rotary Pumps (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Description
【発明の詳細な説明】 産業上の利用分野 本発明は旋回スクロールに枢着され、主軸回転に伴っ
て旋回スクロールを旋回移動させるスクロール圧縮機の
クランク軸構造に関するものである。Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a crankshaft structure of a scroll compressor which is pivotally mounted on an orbiting scroll and orbitally moves the orbiting scroll with rotation of a main shaft.
従来の技術 第５図に示す如く、旋回スクロール７には軸受８を介
しクランク軸1Aが枢着される。クランク軸1Aは主軸（回
転軸）２に偏心して連結形成される。この偏心量が旋回
半径Ｒ（第６図）に相当する。主軸２は軸受５を介しケ
ーシング６に枢支される。ケーシング６に固定する固定
スクロール９は旋回スクロールに係合し吸入媒体を圧縮
すべく作用する。2. Description of the Related Art As shown in FIG. 5, a crankshaft 1A is pivotally attached to an orbiting scroll 7 via a bearing 8. The crankshaft 1A is eccentrically connected to a main shaft (rotating shaft) 2 and formed. This amount of eccentricity corresponds to the turning radius R (FIG. 6). The main shaft 2 is pivotally supported by a casing 6 via a bearing 5. A fixed scroll 9 fixed to the casing 6 acts on the orbiting scroll to compress the suction medium.
従来、第５図に示すが如きスクロール圧縮機において
は、第６図および第７図に示すが如き構造の主軸２およ
びクランク軸1Aが一般であった。Conventionally, in a scroll compressor as shown in FIG. 5, a main shaft 2 and a crankshaft 1A having a structure as shown in FIGS. 6 and 7 were generally used.
発明が解決しようとする問題点 第６図に示す如く、主軸２の中心点をO1とし、クラン
ク軸1Aの中心点をO2とすると、中心点O1およびO2間の距
離が旋回半径Ｒを表わす。主軸２には前記の如く、軸受
５が挿着されるが、軸受５をクランク軸1A側から取り外
す場合が多い。従って、仮りにクランク軸1Aの外周が主
軸２の外周から食み出している場合には軸受５を主軸２
から取り外すことができなくなる。そこでクランク軸1A
の外径をd1,主軸２の外径をd2とすると、両者の間にはd
2≧2Rの関係式が成立する。従って旋回半径Ｒが定ま
り、強度上の要請から直径d1の寸法が決まると、直径d2
は必然的に決定される。軸受５は直径d2により決まり、
ケーシング６の寸法も軸受５に左右される。このため必
要以上の寸法の主軸２および軸受５が使用される場合が
生ずると共に、ケーシング６も大型となり、機械が大型
で高価のものとなる不具合が生ずる。Problems to be Solved by the Invention As shown in FIG. 6, when the center point of the main shaft 2 is O 1 and the center point of the crankshaft 1A is O 2 , the distance between the center points O 1 and O 2 is the turning radius. Represents R. The bearing 5 is inserted into the main shaft 2 as described above, but the bearing 5 is often removed from the crankshaft 1A side. Therefore, if the outer periphery of the crankshaft 1A protrudes from the outer periphery of the main shaft 2, the bearing 5 is connected to the main shaft 2A.
Can not be removed from the So crankshaft 1A
If the outside diameter of the shaft 2 is d 1 and the outside diameter of the spindle 2 is d 2 , d
The relational expression of 2 ≧ 2R holds. Therefore, when the turning radius R is determined and the dimension of the diameter d 1 is determined from the requirement for strength, the diameter d 2
Is inevitably determined. The bearing 5 is determined by the diameter d 2,
The dimensions of the casing 6 also depend on the bearing 5. For this reason, the main shaft 2 and the bearing 5 having dimensions larger than necessary may be used, and the casing 6 may be large in size, resulting in a problem that the machine is large and expensive.
本発明は前記不具合等を解決するもので、所定諸元の
制約下において、クランク軸，主軸，軸受，ケーシング
等の寸法，形状を必要にして十分の寸法のものから形成
せしめ、機械の軽量化とコスト低減を図るに好適なスク
ロール圧縮機のクランク軸構造を提供することにある。The present invention solves the above-mentioned disadvantages and the like. Under the constraints of predetermined specifications, the dimensions and shapes of the crankshaft, the main shaft, the bearings, the casing, and the like are required and formed from those having sufficient dimensions to reduce the weight of the machine. Another object of the present invention is to provide a scroll compressor crankshaft structure suitable for reducing costs.
問題点を解決するための手段 本発明はこのために、スクロール圧縮機のケーシング
（６）のほぼ中心に配設され軸受（５）により支持され
る直径d2の主軸（２）と、この一端側に一体的に形成さ
れ旋回半径Ｒだけ偏心して形成され旋回スクロール
（７）に枢着される直径d1のクランク軸（１）を有し、
前記クランク軸（１）と主軸（２）とがd1/2＋Ｒ＞d2/2
の関係に形成されるスクロール圧縮機のクランク軸構造
において、前記クランク軸（１）の前記主軸（２）との
連結部位からクランク軸（２）の先端側に向かって前記
軸受（５）の巾寸法よりも少なくとも小さくない範囲に
ネック部４を形成し、該ネック部４の外周を前記主軸
（２）の外周から少なくとも出張らない形状に形成して
なるスクロール圧縮機のクランク軸構造を構成するもの
である。For the means present invention for solving the problems this, almost disposed around the bearing (5) of diameter d 2 which is supported by the main shaft of the casing of the scroll compressor (6) (2), one end has an integrally formed turning radius R by eccentrically formed orbiting scroll (7) to the crank shaft of diameter d 1 which is pivotally mounted (1) on the side,
The crankshaft (1) and spindle (2) and is d 1/2 + R> d 2/2
In the crankshaft structure of the scroll compressor formed in the relationship of (1), the width of the bearing (5) from the connecting portion of the crankshaft (1) with the main shaft (2) toward the tip end of the crankshaft (2). A neck portion 4 is formed at least in a range not smaller than the dimension, and a crankshaft structure of a scroll compressor is formed in which the outer periphery of the neck portion 4 is formed in a shape that does not travel at least from the outer periphery of the main shaft (2). Things.
作用 クランク軸を主軸外周より食み出す寸法に形成し得る
ため、従来に較べて大径のクランク軸が形成され、主
軸，軸受等を大径のものにしなくとも強度的に十分なク
ランク軸を形成することができる。また主軸を枢支する
軸受の巾寸法以上にクランク軸の外周の食み出し部が削
除されているためおよびクランク軸が主軸より小径に形
成されているためとにより軸受をクランク軸側から取り
外すことが可能となる。Action Since the crankshaft can be formed so as to protrude from the outer periphery of the main shaft, a crankshaft having a larger diameter than before is formed, and a crankshaft having sufficient strength can be obtained without using a large diameter main shaft and bearings. Can be formed. Also, the bearing must be removed from the crankshaft side because the protruding portion on the outer periphery of the crankshaft has been removed more than the width dimension of the bearing that pivotally supports the main shaft, and because the crankshaft has a smaller diameter than the main shaft. Becomes possible.
実施例 以下、本発明の実施例を図面に基づき説明する。Embodiment An embodiment of the present invention will be described below with reference to the drawings.
第１図に示す如く、主軸２の中心点O1とクランク軸１
の中心点O2間の距離、すなわち旋回半径Ｒが決められた
として、中心点O2を中心として直径d3の円を画き、クラ
ンク軸１の直径d3を決める。直径d3が第７図の直径d1よ
り大径の場合には食み出し部３だけ主軸２の外周よりク
ランク軸１は食み出す。第２図に示す如く、クランク軸
１の外周の内、主軸２との連結端Ｂから主軸２の軸受５
の巾寸法以上軸線方向に沿って離れた位置Ｃまでの食み
出し部３を削除し、ネック部４を形成する。第３図はネ
ック部４を示すもので円の一部がカットされた断面形状
となる。食み出し部３を削除することによりネック部４
の外周と主軸２の外周は同一面上にくることになる。As shown in FIG. 1, the center point O 1 of the main shaft 2 and the crank shaft 1
The distance between the center point O 2, that as the turning radius R is determined, Egaki a circle having a diameter d 3 around the center point O 2, determines the diameter d 3 of the crankshaft 1. Crankshaft 1 from the outer periphery of the protruding portion 3 by the main shaft 2 when the diameter d 3 of larger diameter than the diameter d 1 of Figure 7 is protruded. As shown in FIG. 2, a bearing 5 of the main shaft 2 extends from a connection end B with the main shaft 2 in the outer periphery of the crankshaft 1.
The protruding portion 3 up to the position C separated in the axial direction by the width dimension or more is removed, and the neck portion 4 is formed. FIG. 3 shows the neck portion 4 and has a cross-sectional shape in which a part of a circle is cut. By removing the protruding part 3, the neck part 4 is removed.
And the outer circumference of the main shaft 2 are on the same plane.
以上の如く、クランク軸１を形成することによりクラ
ンク軸１は従来のクランク軸1Aに較べて主軸２が同一径
の状態であっても大径のものから形成される。これによ
り、クランク軸１の強度が保持されると共に、主軸2,軸
受５およびケーシング６が小型に形成される。As described above, by forming the crankshaft 1, the crankshaft 1 is formed with a larger diameter than the conventional crankshaft 1A even if the main shaft 2 has the same diameter. Thereby, the strength of the crankshaft 1 is maintained, and the main shaft 2, the bearing 5, and the casing 6 are formed in a small size.
第４図は軸受５を主軸２から取り外す状態を示すもの
で、ネック部４と主軸２とが同一面上にあるため、軸受
５はネック部４側に抜け出し可能となる。ネック部４ま
で抜けた軸受５は２点鎖線に示す如く、主軸２より小径
のクランク軸１を通り抜け可能のため簡単に取り外しで
きることになる。FIG. 4 shows a state in which the bearing 5 is detached from the main shaft 2. Since the neck portion 4 and the main shaft 2 are on the same plane, the bearing 5 can come out to the neck portion 4 side. The bearing 5 which has been pulled out to the neck portion 4 can pass through the crankshaft 1 having a smaller diameter than the main shaft 2 as shown by a two-dot chain line, so that it can be easily removed.
前記実施例において、ネック部４を主軸２の外周と同
一面に形成したが、ネック部４は主軸２の外周から張み
出さなければよく、主軸２の外周から引っ込んで（すな
わち外周面以下に）形成されるものであればよい。但
し、ネック部４におけるクランク軸１の断面積はすくな
くともクランク軸１に負荷される外力に耐える強度を有
する寸法に形成されることが必要とされる。In the above-described embodiment, the neck portion 4 is formed on the same surface as the outer periphery of the main shaft 2. However, the neck portion 4 does not need to protrude from the outer periphery of the main shaft 2, and is retracted from the outer periphery of the main shaft 2 (that is, the outer peripheral surface or lower). ) Any material may be used. However, it is necessary that the cross-sectional area of the crankshaft 1 in the neck portion 4 be formed to have a size that has strength enough to withstand an external force applied to the crankshaft 1.
発明の効果 以上の説明によって明らかな如く、本発明によれば偏
心量等の諸元の制約の中でクランク軸，主軸，軸受等を
必要にして十分な形状のものから形成可能にし、かつ機
械の大型化を防止し、軽量化，コスト低減を可能にする
効果が上げられる。As is clear from the above description, according to the present invention, the crankshaft, the main shaft, the bearings, and the like can be formed from a sufficient shape, and the machine can be formed under the constraints of the specifications such as the amount of eccentricity. The effect of preventing an increase in the size of the device and reducing the weight and cost can be obtained.
第１図は本発明一実施例の正面図、第２図は第１図の側
面図、第３図は第２図のIII−III線断面図、第４図は実
施例の作用を説明する説明用側面図、第５図はクランク
軸と旋回スクロールとの取付け状態を示す部分断面図、
第６図は従来のクランク軸と主軸の関係を示す正面図、
第７図は第６図の側面図である。 1,1A……クランク軸、２……主軸、３……食み出し部、
４……ネック部、5,8……軸受、６……ケーシング、７
……旋回スクロール、９……固定スクロール。1 is a front view of one embodiment of the present invention, FIG. 2 is a side view of FIG. 1, FIG. 3 is a sectional view taken along line III-III of FIG. 2, and FIG. Fig. 5 is a side view for explanation, Fig. 5 is a partial cross-sectional view showing a mounted state of the crankshaft and the orbiting scroll,
FIG. 6 is a front view showing a relationship between a conventional crankshaft and a main shaft,
FIG. 7 is a side view of FIG. 1, 1A ... crankshaft, 2 ... main shaft, 3 ... protruding part,
4 Neck, 5, 8 Bearing, 6 Casing, 7
... orbiting scroll, 9 ... fixed scroll.
Claims (1)
ぼ中心に配設され軸受（５）により支持される直径d2の
主軸（２）と、この一端側に一体的に形成され旋回半径
Ｒだけ偏心して形成され旋回スクロール（７）に枢着さ
れる直径d1のクランク軸（１）を有し、前記クランク軸
（１）と主軸（２）とがd1/2＋Ｒ＞d2/2の関係に形成さ
れるスクロール圧縮機のクランク軸構造において、前記
クランク軸（１）の前記主軸（２）との連結部位からク
ランク軸（２）の先端側に向かって前記軸受（５）の巾
寸法よりも少なくとも小さくない範囲にネック部４を形
成し、該ネック部４の外周を前記主軸（２）の外周から
少なくとも出張らない形状に形成することを特徴とする
スクロール圧縮機のクランク軸構造。1. A substantially centered disposed in a bearing (5) of diameter d 2 which is supported by the main shaft (2), the turning radius R is integrally formed on one end side of the casing of the scroll compressor (6) only formed eccentrically has an orbiting scroll crankshaft diameter d 1 which is pivotally connected to (7) (1), the crankshaft (1) and spindle (2) and is d 1/2 + R> d 2/2 In the crankshaft structure of the scroll compressor formed in the relationship of (1), the width of the bearing (5) from the connecting portion of the crankshaft (1) with the main shaft (2) toward the tip end of the crankshaft (2). A crankshaft structure for a scroll compressor, characterized in that the neck portion (4) is formed at least in a range not smaller than the size, and the outer periphery of the neck portion (4) is formed in a shape that does not travel at least from the outer periphery of the main shaft (2). .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22958286A JP2572215B2 (en) | 1986-09-30 | 1986-09-30 | Crankshaft structure of scroll compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22958286A JP2572215B2 (en) | 1986-09-30 | 1986-09-30 | Crankshaft structure of scroll compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6388290A JPS6388290A (en) | 1988-04-19 |
| JP2572215B2 true JP2572215B2 (en) | 1997-01-16 |
Family
ID=16894438
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP22958286A Expired - Lifetime JP2572215B2 (en) | 1986-09-30 | 1986-09-30 | Crankshaft structure of scroll compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2572215B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6872062B2 (en) | 2003-01-21 | 2005-03-29 | Fujitsu General Limited | Scroll compressor |
-
1986
- 1986-09-30 JP JP22958286A patent/JP2572215B2/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6872062B2 (en) | 2003-01-21 | 2005-03-29 | Fujitsu General Limited | Scroll compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6388290A (en) | 1988-04-19 |
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