JPS5825594A - Rotary shaft for totally-closed motor compressor - Google Patents
Rotary shaft for totally-closed motor compressorInfo
- Publication number
- JPS5825594A JPS5825594A JP12571882A JP12571882A JPS5825594A JP S5825594 A JPS5825594 A JP S5825594A JP 12571882 A JP12571882 A JP 12571882A JP 12571882 A JP12571882 A JP 12571882A JP S5825594 A JPS5825594 A JP S5825594A
- Authority
- JP
- Japan
- Prior art keywords
- steel pipe
- shaft
- spiral groove
- pipe shaft
- bore
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
- F04B39/0223—Lubrication characterised by the compressor type
- F04B39/023—Hermetic compressors
- F04B39/0238—Hermetic compressors with oil distribution channels
- F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は軸部及び偏心部を一個の鋼管の塑性加工により
構成する回転軸C以下、鋼管軸)の給油ポンプの構造に
関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to the structure of an oil supply pump having a shaft portion and an eccentric portion formed by plastic working of a single steel tube.
第1図は鋼管を基本素材とする一般的な鋼管軸の形態を
示すもので、1は回転軸、回転軸1は軸心回転する軸部
1aと偏心部1bに大別され、この両者は塑性加工によ
る段曲げ部1Cで連結した一個の鋼管で成形している。Fig. 1 shows the form of a general steel pipe shaft made of steel pipe as the basic material. 1 is a rotating shaft, and the rotating shaft 1 is roughly divided into a shaft part 1a that rotates around the axis and an eccentric part 1b, both of which are It is formed from a single steel pipe connected by a stepped bent portion 1C formed by plastic working.
また、軸部1aの上部には圧縮機構部の運転により発生
するアンバランスを吸収するバランスウェイト2が付属
する。また、軸部1a、偏心部1bには油入1d、油溝
1e、油溜す部1fが形成されている。鋼管軸の先端は
図示の如く口絞りした形態の給油ポンプ部1gが形成さ
れ、しかも口絞り部内壁と潤滑油のスリップにより給油
量の低下を防止する目的の平押し形状部1hが成形され
ている。Further, a balance weight 2 is attached to the upper part of the shaft portion 1a to absorb the unbalance caused by the operation of the compression mechanism portion. Further, an oil filler 1d, an oil groove 1e, and an oil reservoir 1f are formed in the shaft portion 1a and the eccentric portion 1b. As shown in the figure, the tip of the steel pipe shaft is formed with an oil supply pump part 1g having a constricted opening, and a flat pressed part 1h for the purpose of preventing a decrease in the amount of oil supplied due to slippage of the lubricating oil with the inner wall of the constricted part. There is.
口絞り形状は潤滑油に遠心力を付加する目的から鋼管軸
内径の約1h程度の口絞り径を採用しているのが通例で
、鋼管軸の回転に伴い矢印で示す様に潤滑油が各部に供
給される。しかし、第1図に示す様に鋼管軸に口絞り形
状を成形した給油ポンプ構造は、鋼管自体の肉厚或いは
材質によっても多少異なるが、口絞り加工の加工硬化、
更に塑性加工の応力的にアンバランスな平押し部1hを
形成することから、成形時に割れが生じ所期の給油ポン
プ機能を発揮出来ない場合がある。また、塑性成形に要
する荷重がいきおい大きくなることから、この鋼管軸の
成形を多ステーションのトランスファープレスとする場
合に於て、成形荷重のアンバランスが発生し、全体的な
成形精度を劣化する場合がある。For the purpose of applying centrifugal force to the lubricating oil, the orifice diameter is usually about 1 h of the inner diameter of the steel pipe shaft, and as the steel pipe shaft rotates, the lubricating oil flows into various parts as shown by the arrows. supplied to However, as shown in Fig. 1, the oil pump structure in which a neck-drawn shape is formed on the steel pipe shaft is not easy to use due to the work hardening of the neck-drawing process, although it varies somewhat depending on the wall thickness and material of the steel pipe itself.
Furthermore, since the flat pressed portion 1h is formed with an unbalanced stress during plastic working, cracks may occur during molding and the intended oil pump function may not be achieved. In addition, since the load required for plastic forming becomes extremely large, when forming this steel pipe shaft using a multi-station transfer press, an imbalance in the forming load may occur and the overall forming accuracy may deteriorate. There is.
従って、本発明はこれら塑性加工上の問題とそれによっ
て発生する性能的欠陥を補うことを目的とするものであ
る。Therefore, the present invention aims to compensate for these problems in plastic working and the performance defects caused thereby.
第2図は本発明に係わる鋼管軸の一例を示すもので、軸
部1aと同径寸法の鋼管軸1先端内径に鋼管軸の回転方
向により漸時上昇する方向の蝉線状スパイラル溝11を
成形する。スパイラル溝ハ機械加工(タッピング方式)
或いは第2図に示す断面となる様な塑性加工で成形する
。FIG. 2 shows an example of a steel pipe shaft according to the present invention, in which a spiral groove 11 is formed on the inner diameter of the tip end of the steel pipe shaft 1 having the same diameter as the shaft portion 1a in a direction that gradually rises according to the rotational direction of the steel pipe shaft. Shape. Spiral groove machining (tapping method)
Alternatively, it is formed by plastic working so as to have the cross section shown in FIG.
その結果、鋼管軸1の回転により内壁側に遠心力の影響
で押し付けられる潤滑油がスパイラル溝11で掬い上げ
られ、矢印の如く鋼管軸1内径上部に連続して供給され
、従来潤滑油の粘性を口絞り内径傾斜面で潤滑油を供給
する方式に比較し、鋼管内壁と潤滑油間の摩擦係数が上
昇し、圧縮機運転による油温上昇等に伴う粘性低下によ
るスリップ現象を抑止出来る。即ち、第5図は塑性加工
上置も有利な単純なテーバの口絞り形状の給油ポンプ(
第1図から平押し部を除いた形状)で油温な給油特性に
改善される。また、第4図に示す様にある範囲の回転数
で全く給油が停止するか、或いは減少する給油特性a線
がb線に示す様に改善される。加工上から見ると切削法
或いは塑性加工法の何れによるスパイラル溝成形でも加
工応力的には口絞り成形、引いて平押し成形の何れの加
工応力よりも低く製造のトラブルは充分解消され勿論割
れ発生の危険は回避される。特に塑性加工で成形される
第6図に示すスパイラル溝は切粉発生のない高効率成形
法であり、これらの特許効果は性能改善加工特性上有利
である。As a result, the lubricating oil that is pressed against the inner wall by the centrifugal force due to the rotation of the steel pipe shaft 1 is scooped up by the spiral groove 11 and continuously supplied to the upper part of the inner diameter of the steel pipe shaft 1 as shown by the arrow. Compared to a method in which lubricating oil is supplied through a slanted internal diameter surface, the coefficient of friction between the inner wall of the steel pipe and the lubricating oil increases, and it is possible to prevent slippage caused by a decrease in viscosity due to increases in oil temperature caused by compressor operation. In other words, Fig. 5 shows an oil supply pump (with a simple Taber neck shape) which is also advantageous for plastic working.
The shape shown in Fig. 1 with the flat pressed part removed) improves the oil supply characteristics with a lower oil temperature. Furthermore, as shown in FIG. 4, the oil supply characteristic, line a, in which oil supply stops or decreases at a certain rotation speed, is improved as shown in line b. From a processing perspective, the processing stress of spiral groove forming using either the cutting method or the plastic processing method is lower than that of either mouth drawing or flat pressing, which sufficiently eliminates manufacturing problems and, of course, causes cracks. danger is avoided. In particular, the spiral groove shown in FIG. 6 formed by plastic working is a highly efficient forming method that does not generate chips, and these patented effects are advantageous in terms of performance improvement and processing characteristics.
第1図は、従来公知鋼管軸の形状の一例を示す斜視図、
第2図は本発明に係わる鋼管軸の一例を示す斜視図、第
6図は鋼管の内径(一点破線)を有効径とする塑性成形
溝の形状の一例を示す第2図A−A線に沿った断面図、
第4図及び第5図は本発明に係わる鋼管軸と、従来公知
であった単純テーバロ絞りポンプの給油特性を示す絵図
である1・・・鋼管軸、1a・・・鋼管軸1の軸部、1
b・・・鋼管軸1の偏心部、1C・・・段曲げ部、1d
・・・?白人、1e・・・油溝、1f・・・油溜り部、
1g・・・給油ポンプ。
部、1 h”・・・平押し部、11・・・スパイラル溝
。
!34図
!35図
潰−/j!LFIG. 1 is a perspective view showing an example of the shape of a conventionally known steel pipe shaft;
Fig. 2 is a perspective view showing an example of a steel pipe shaft according to the present invention, and Fig. 6 is a perspective view showing an example of the shape of a plastic forming groove whose effective diameter is the inner diameter of the steel pipe (dotted line). Cross-sectional view along
4 and 5 are pictorial diagrams showing the oil supply characteristics of a steel pipe shaft according to the present invention and a conventionally known simple Tebaro throttle pump. 1... Steel pipe shaft, 1a... Shaft part of steel pipe shaft 1 ,1
b...Eccentric part of steel pipe shaft 1, 1C...Step bent part, 1d
...? White person, 1e...oil groove, 1f...oil sump part,
1g...Refueling pump. Part, 1 h"...Flat press part, 11...Spiral groove. !34 figure!35 figure crushed-/j!L
Claims (1)
内径を給油ポンプとなす回転軸に於て、回転軸内径に回
転方向に対し輝線上昇するスパイラル溝を成形し、ポン
プ機能部を形成したことを特徴とする全密閉形電動圧縮
機用回転軸。The rotating shaft of the compressor is made of a plastically processed steel pipe, and the inner diameter of the steel pipe serves as the oil supply pump.A spiral groove whose bright line rises in the direction of rotation is formed on the inner diameter of the rotating shaft to form a pump function part. A rotary shaft for a completely hermetic electric compressor, which is characterized by:
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP12571882A JPS5825594A (en) | 1982-07-21 | 1982-07-21 | Rotary shaft for totally-closed motor compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP12571882A JPS5825594A (en) | 1982-07-21 | 1982-07-21 | Rotary shaft for totally-closed motor compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS5825594A true JPS5825594A (en) | 1983-02-15 |
Family
ID=14917030
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP12571882A Pending JPS5825594A (en) | 1982-07-21 | 1982-07-21 | Rotary shaft for totally-closed motor compressor |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5825594A (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1999032790A3 (en) * | 1997-12-22 | 1999-09-02 | Brasil Compressores Sa | A reciprocating hermetic compressor |
WO2003052271A1 (en) * | 2001-12-17 | 2003-06-26 | Lg Electronics Inc. | Crank shaft in dual capacity compressor |
WO2005078282A1 (en) * | 2004-02-11 | 2005-08-25 | Arcelik Anonim Sirketi | A compressor |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4820005B1 (en) * | 1969-06-30 | 1973-06-18 | ||
JPS4932328U (en) * | 1972-06-23 | 1974-03-20 | ||
JPS5267011A (en) * | 1975-11-28 | 1977-06-03 | Hitachi Ltd | Totally-enclosed type electric compressor |
JPS5364809A (en) * | 1976-11-22 | 1978-06-09 | Hitachi Ltd | Manufacturing method of crankshaft of compressor |
-
1982
- 1982-07-21 JP JP12571882A patent/JPS5825594A/en active Pending
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4820005B1 (en) * | 1969-06-30 | 1973-06-18 | ||
JPS4932328U (en) * | 1972-06-23 | 1974-03-20 | ||
JPS5267011A (en) * | 1975-11-28 | 1977-06-03 | Hitachi Ltd | Totally-enclosed type electric compressor |
JPS5364809A (en) * | 1976-11-22 | 1978-06-09 | Hitachi Ltd | Manufacturing method of crankshaft of compressor |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1999032790A3 (en) * | 1997-12-22 | 1999-09-02 | Brasil Compressores Sa | A reciprocating hermetic compressor |
WO2003052271A1 (en) * | 2001-12-17 | 2003-06-26 | Lg Electronics Inc. | Crank shaft in dual capacity compressor |
US7100743B2 (en) | 2001-12-17 | 2006-09-05 | Lg Electronics Inc. | Crank shaft in dual capacity compressor |
WO2005078282A1 (en) * | 2004-02-11 | 2005-08-25 | Arcelik Anonim Sirketi | A compressor |
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