JPH0217726B2 - - Google Patents
Info
- Publication number
- JPH0217726B2 JPH0217726B2 JP59110424A JP11042484A JPH0217726B2 JP H0217726 B2 JPH0217726 B2 JP H0217726B2 JP 59110424 A JP59110424 A JP 59110424A JP 11042484 A JP11042484 A JP 11042484A JP H0217726 B2 JPH0217726 B2 JP H0217726B2
- Authority
- JP
- Japan
- Prior art keywords
- web
- crankshaft
- hole
- crank
- crank pin
- 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
- 239000000463 material Substances 0.000 claims description 8
- 238000010008 shearing Methods 0.000 claims 1
- 230000000452 restraining effect Effects 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000002788 crimping Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 229910000760 Hardened steel Inorganic materials 0.000 description 1
- 229910001209 Low-carbon steel Inorganic materials 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 102200082816 rs34868397 Human genes 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
-
- 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
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
- F16C3/06—Crankshafts
- F16C3/10—Crankshafts assembled of several parts, e.g. by welding by crimping
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Ocean & Marine Engineering (AREA)
- Mechanical Engineering (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
- Forging (AREA)
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明はクランクシヤフトに係り、特に構成部
品を塑性変形結合するに好適な構成のクランクシ
ヤフトに関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to a crankshaft, and particularly to a crankshaft having a structure suitable for plastically deforming coupling of component parts.
機関の出力をクランクシヤフトに伝達し、その
回転力により機関点火電源及び点灯負荷電源用磁
石発電機の回転子あるいは冷却フアン等を駆動す
ることは例えば実開昭56−138787号公報等で広く
知られている。
It is widely known, for example, in Japanese Utility Model Application No. 56-138787, that the output of the engine is transmitted to the crankshaft and the rotational force is used to drive the rotor or cooling fan of the magnet generator for the engine ignition power source and the lighting load power source. It is being
ところが前記クランクシヤフトはクランク主軸
とウエブを同一材料から加工成形して形成し、材
質の硬いクランクピンのみを嵌着固定する構造が
とられているが、クランクシヤフトとウエブの成
形がむずかしく生産性の点で不利なものであつ
た。又クランクピンは圧着による嵌着固定である
ため両持ちタイプのクランクシヤフトでは効果を
発揮するが、近年のように小形化のため片持ちに
するタイプでは曲げ応力がかかり非常に信頼性の
点で劣る。 However, the crankshaft has a structure in which the crankshaft and the web are formed by processing and forming the same material, and only the hard crank pin is fitted and fixed, but forming the crankshaft and the web is difficult and reduces productivity. It was disadvantageous in some respects. Also, since the crank pin is fixed by fitting by crimping, it is effective for double-sided crankshafts, but in recent years, cantilever type crankshafts due to miniaturization are subject to bending stress and are extremely unreliable. Inferior.
その他三部品を各々別個に形成し、それらを一
体に組付け固着する構造も提案されているが、い
ずれにしても圧着あるいは溶接固定が用いられて
おり、信頼性、生産性の点で劣る。 A structure in which the three other parts are formed separately and then assembled and fixed together has also been proposed, but in either case, crimping or welding is used, which is inferior in terms of reliability and productivity.
本発明の目的は、小形軽量で信頼性の高い片持
タイプのクランクシヤフトを提供するにある。
An object of the present invention is to provide a cantilever type crankshaft that is small, lightweight, and highly reliable.
本発明はウエブの中心と一体的関係にあるクラ
ンク主軸と、前記ウエブ背面の偏心位置に配置さ
れ、該ウエブと一体関係にあるクランクピンとか
らなるクランクシヤフトであつて、前記ウエブ中
心の一方面に形成された第１の凹穴と、該凹穴よ
り小径でウエブ中心に設けられた貫通孔と、前記
ウエブの反対面の偏心した位置に形成された第２
の凹穴と、前記それぞれの凹穴の内周面に対向す
る周面に環状溝を形成して該凹穴に嵌合され、か
つ前記環状溝に局部的に塑性変形されたウエブ材
により緊迫力と剪断力をもつて結合されているク
ランク主軸とクランクピンとから構成されること
を特徴としたクランクシヤフトにある。
The present invention provides a crankshaft comprising a crank main shaft that is in an integral relationship with the center of a web, and a crank pin that is arranged at an eccentric position on the back surface of the web and is in an integral relationship with the web. a first recessed hole formed, a through hole smaller in diameter than the recessed hole and provided at the center of the web, and a second hole formed at an eccentric position on the opposite surface of the web.
a recessed hole, and an annular groove is formed on the circumferential surface opposite to the inner circumferential surface of each of the recessed holes, and the web material is fitted into the recessed hole and is locally plastically deformed in the annular groove. A crankshaft is characterized in that it is composed of a crank main shaft and a crank pin that are connected with force and shear force.
以下本発明の一実施例を第１図〜第５図により
説明する。
An embodiment of the present invention will be described below with reference to FIGS. 1 to 5.
第１図は片持ちタイプのクランクシヤフトの一
部を断面した全体図で、軟鋼（S45C）からなる
クランク主軸１と円板状のウエブ２と、ハダ焼鋼
からなるクランクピン３とから構成され、各々は
金属の塑性変形圧により強固に結合されている。 Figure 1 is a partially cross-sectional overall view of a cantilever type crankshaft, which is composed of a crank shaft 1 made of mild steel (S45C), a disc-shaped web 2, and a crank pin 3 made of hardened steel. , each is firmly connected by the plastic deformation pressure of the metal.
ウエブ２はその一方面中心にクランク主軸を嵌
合する大径の第１の凹穴２１と、反対面の偏心し
た位置に形成されクランクピン３を嵌合する小径
の第２の凹穴２２とを有し、この両穴は端面に垂
直で軸線に平行になる如く切削等により形成され
ている。又、第１の凹穴２１の底面には、該凹穴
径２１の1/3径の貫通孔２３が形成されている。
一方クランク主軸１とクランクピン３はその元部
の各々凹穴２１，２２の内周面と対向する面に環
状の断面Ｗ溝１１，３１を形成し、それによつて
中間に係合突起１２，３２を形成している。 The web 2 has a large-diameter first recessed hole 21 in the center of one side into which the crankshaft fits, and a small-diameter second recessed hole 22 formed at an eccentric position on the opposite side into which the crank pin 3 is fitted. Both holes are formed by cutting or the like so as to be perpendicular to the end face and parallel to the axis. Further, a through hole 23 having a diameter of 1/3 of the diameter of the first recessed hole 21 is formed in the bottom surface of the first recessed hole 21 .
On the other hand, the crank main shaft 1 and the crank pin 3 have annular cross-section W grooves 11 and 31 formed on the surfaces facing the inner circumferential surfaces of the recessed holes 21 and 22 at their base parts, respectively, so that the engaging protrusions 12 and 31 are formed in the middle. 32 is formed.
上記構成部品は先ず、ウエブ２の凹穴２１にク
ランク主軸１の元部を嵌合した状態で、クランク
主軸の周囲のウエブの材料を端面から金型（図示
せず）で垂直に局部的に押圧する。するとウエブ
材料はＷ溝１１に直角に塑性流動し、Ｗ溝によつ
て生じた係合突起１２によつて局部的に塑性変形
され、そこに発生する高い緊迫力によつて両者間
は強固に結合される。他方クランクピン３も前記
クランク主軸１と同様Ｗ溝３１、係合突起３２を
利用して塑性結合される。ただ前記したクランク
主軸１の場合はウエブ２の中心に固設されるため
金型によりウエブに変形圧を加えると変形応力は
放射状に均等に分布し、規定位置に垂直に結合固
定されるが、クランクピン３の場合は前記したと
おり偏心した位置にあるため、塑性変形圧を加え
た場合は塑性流動バランスがくずれ、第６図鎖線
で示す如く外周方向にピンがμだけ倒れることに
なる。 To manufacture the above component, first, with the base of the crank spindle 1 fitted into the recessed hole 21 of the web 2, the material of the web around the crank spindle is vertically and locally cut from the end surface using a mold (not shown). Press. Then, the web material plastically flows perpendicular to the W groove 11, is locally plastically deformed by the engaging protrusion 12 generated by the W groove, and the high tension force generated therein makes the bond between the two firm. be combined. On the other hand, the crank pin 3 is also plastically coupled using the W groove 31 and the engagement protrusion 32 in the same manner as the crank main shaft 1. However, in the case of the above-mentioned crank shaft 1, since it is fixed at the center of the web 2, when deformation pressure is applied to the web by a mold, the deformation stress is evenly distributed radially, and the crank shaft 1 is fixed vertically at a specified position. In the case of the crank pin 3, as described above, since it is in an eccentric position, when plastic deformation pressure is applied, the plastic flow balance is disrupted, and the pin falls in the outer circumferential direction by μ as shown by the chain line in FIG.
ところで本発明の実施例の場合は、予めウエブ
２の中心に貫通孔２３を設けてある。即ち貫通孔
のない場合は中心方向で塑性変形拘束力が強く、
極力拘束力の小さい外周方向側に材料が塑性流動
しようとするためピン倒れが発生しやすいが、貫
通孔２３を設けることにより中心軸方向も塑性変
形拘束力が弱められ、塑性流動バランスが良くな
るためクランクピン周囲にも均等に塑性変形圧が
加わりピン倒れが減少する。 By the way, in the case of the embodiment of the present invention, the through hole 23 is provided in the center of the web 2 in advance. In other words, when there is no through hole, the plastic deformation restraining force is strong in the center direction,
Pin collapse is likely to occur because the material tries to plastically flow toward the outer circumferential direction where the restraining force is as small as possible, but by providing the through hole 23, the plastic deformation restraining force is also weakened in the central axis direction, improving the plastic flow balance. Therefore, plastic deformation pressure is applied evenly around the crank pin, reducing pin collapse.
上記貫通孔２３とクランクピン倒れ（μ）との
関係を考察してみると、第６図にその結果を示し
てあるとおり、孔なしでは塑性流動のアンバラン
スから約30（μ）あつたに対し、1/4Ｄの孔では10
（μ）、更に1/2Ｄでは５（μ）以下となり非常に効
果的であることが解つた。しかし逆に孔径が大き
く、余りにクランクピン３に接近すると中心側が
逆に弱くなつて塑性流動バランスがくずれ反対方
向に倒れやすくなり好ましくない。 When we consider the relationship between the through hole 23 and the crank pin tilt (μ), as shown in Fig. 6, it is found that without the hole, the crank pin collapses by about 30 (μ) due to the unbalanced plastic flow. On the other hand, a 1/4D hole has 10
(μ), and 5 (μ) or less at 1/2D, which was found to be very effective. However, on the other hand, if the hole diameter is large and it gets too close to the crank pin 3, the center side will become weaker, the plastic flow balance will be disrupted, and it will be more likely to fall in the opposite direction, which is not preferable.
第２図、第３図はクランク主軸１の各々断面図
で径の異なる部分にそれぞれ係合突起１３，１４
を形成していることを示してある。 FIGS. 2 and 3 are cross-sectional views of the crank main shaft 1, with engaging protrusions 13 and 14 at portions with different diameters, respectively.
It is shown that it forms.
上記係合突起は、第３図を例にとつて説明する
ならばd1なる径の主軸の外周に直角面を有する金
型を押圧することによつて形成された巾l1の大な
る突起１３と、巾l2の小なる突起１４とが対称位
置に形成されている。一方第４図は前記係合突起
１３，１４に係合される被係合物（回転子ボス
等）４で、前記係合突起１３，１４に適合する寸
法関係の溝４１と４２が形成されている。 The above-mentioned engagement protrusion is a large protrusion with a width l1 formed by pressing a mold having a surface perpendicular to the outer periphery of a main shaft having a diameter d1 . 13 and a small protrusion 14 having a width l 2 are formed at symmetrical positions. On the other hand, FIG. 4 shows an engaged object (such as a rotor boss) 4 that is engaged with the engagement protrusions 13 and 14, and grooves 41 and 42 are formed with dimensions that match the engagement protrusions 13 and 14. ing.
即ち、l1＞l2 L1＞L2の突起巾を備えていると
共に、
l1L1，l2L2
の寸法関係となつている。 That is, it has a projection width of l 1 >l 2 L 1 >L 2 and a dimensional relationship of l 1 L 1 and l 2 L 2 .
上記寸法関係は、被係合物４を規定位置に配置
すると共に回転方向の係合を満足する。もちろん
係合溝４１，４２は係合突起１３，１４の高さよ
り大きくしてあり、挿入時に引掛らないようにし
てある。 The above dimensional relationship satisfies engagement in the rotational direction while arranging the engaged object 4 at a prescribed position. Of course, the engagement grooves 41 and 42 are made larger in height than the engagement protrusions 13 and 14 so that they do not get caught during insertion.
上記実施例によれば、ウエブ２にクランク主軸
及びクランクピン３を垂直に精度よく固定するこ
とができると共に、ウエブ材料を環状係合突起１
２，３２によつて局部的に塑性させ、そこに高い
緊迫力を発生させる構造となつているため結合強
度に優れ、加熱などの必要もないため熱影響もな
く信頼性の高いものとなる。又、各々部品はそれ
ぞれ単純形状なものからなるため、小形軽量で生
産性に優れ、コスト的にも有利である。特にクラ
ンクピン３は耐摩耗性の材料を選んでも塑性変形
結合により強固に結合でき、片持ちタイプのクラ
ンクシヤフトに有効となる。 According to the above embodiment, the crank main shaft and the crank pin 3 can be vertically and accurately fixed to the web 2, and the web material can be fixed to the annular engaging protrusion 1.
2 and 32 to locally plasticize and generate a high tensile force there, the bonding strength is excellent, and since there is no need for heating, it is highly reliable without being affected by heat. In addition, since each component has a simple shape, it is small and lightweight, has excellent productivity, and is advantageous in terms of cost. In particular, even if the crank pin 3 is made of wear-resistant material, it can be firmly connected by plastic deformation bonding, which is effective for cantilever type crankshafts.
更にクランクピン結合精度に効果を発揮する貫
通孔２３は、その後クランクピンのバランス測定
にも利用することができ、その効果は大きい。 Furthermore, the through hole 23, which has an effect on crank pin coupling accuracy, can also be used for later crank pin balance measurement, which is highly effective.
尚、クランク主軸とウエブを予め一体に形成し
たものにクランクピンのみを塑性結合する場合で
も塑性流動バランスは有効で、バランス孔は必要
である。 Incidentally, even when only the crank pin is plastically connected to the crankshaft and the web formed integrally in advance, the plastic flow balance is effective and a balance hole is necessary.
又、環状係合突起１２，３２に細かい凹凸を設
けることによつて更に結合力を増すことができ
る。 Further, by providing the annular engagement protrusions 12 and 32 with fine irregularities, the bonding force can be further increased.
以上本発明によれば、小形軽量で信頼性の高い
片持タイプのクランクシヤフトが提供できる。
As described above, according to the present invention, it is possible to provide a cantilever type crankshaft that is small, lightweight, and highly reliable.
図面は本発明クランクシヤフトの実施例を示す
もので、第１図は要部を断面したクランクシヤフ
トの側面図、第２図は第１図の−断面図、第
３図は第１図の−断面図、第４図は被係合物
の断面図、第５図はウエブの正面図、第６図は第
１図の要部拡大図、第７図は貫通孔とクランクピ
ン倒れとの関係を示すグラフである。
１……クランク主軸、２……ウエブ、３……ク
ランクピン、２１，２２……凹穴、１１，３１…
…環状溝、２３……貫通孔。
The drawings show an embodiment of the crankshaft of the present invention. FIG. 1 is a side view of the crankshaft with main parts cut away, FIG. 2 is a cross-sectional view of FIG. 1, and FIG. 3 is a cross-sectional view of FIG. 1. 4 is a sectional view of the engaged object, FIG. 5 is a front view of the web, FIG. 6 is an enlarged view of the main part of FIG. 1, and FIG. 7 is the relationship between the through hole and crank pin collapse. This is a graph showing. 1... Crank main shaft, 2... Web, 3... Crank pin, 21, 22... Recessed hole, 11, 31...
...Annular groove, 23...through hole.
Claims (1)
軸と、前記ウエブ背面の偏心位置に配置され、該
ウエブと一体関係にあるクランクピンとからなる
クランクシヤフトであつて、前記ウエブ中心の一
方面に形成された第１の凹穴と、該凹穴より小径
でウエブ中心に設けられた貫通孔と、前記ウエブ
の反対面の偏心した位置に形成された第２の凹穴
と、前記それぞれの凹穴の内周面に対向する周面
に環状溝を形成して該凹穴に嵌合され、かつ前記
環状溝に局部的に塑性変形されたウエブ材により
緊迫力と剪断力をもつて結合されているクランク
主軸とクランクピンとから構成されることを特徴
としたクランクシヤフト。 ２ 特許請求の範囲第１項記載において、貫通孔
はクランク主軸直径の1/4〜1/2倍であることを特
徴としたクランクシヤフト。[Scope of Claims] 1. A crankshaft consisting of a crank main shaft that is in an integral relationship with the center of the web, and a crank pin that is arranged at an eccentric position on the back surface of the web and is in an integral relationship with the web, the crankshaft comprising: a first recessed hole formed on one side of the web, a through hole with a smaller diameter than the recessed hole and provided at the center of the web, and a second recessed hole formed at an eccentric position on the opposite side of the web; An annular groove is formed on the circumferential surface opposite to the inner circumferential surface of each of the recessed holes, and tension force and shearing force are applied by a web material that is fitted into the recessed hole and is locally plastically deformed in the annular groove. A crankshaft characterized by being composed of a crank main shaft and a crank pin that are connected together. 2. The crankshaft according to claim 1, wherein the through hole is 1/4 to 1/2 times the diameter of the crankshaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11042484A JPS60256614A (en) | 1984-05-30 | 1984-05-30 | Crankshaft |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11042484A JPS60256614A (en) | 1984-05-30 | 1984-05-30 | Crankshaft |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60256614A JPS60256614A (en) | 1985-12-18 |
| JPH0217726B2 true JPH0217726B2 (en) | 1990-04-23 |
Family
ID=14535402
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP11042484A Granted JPS60256614A (en) | 1984-05-30 | 1984-05-30 | Crankshaft |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60256614A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2017000129A1 (en) * | 2015-06-29 | 2017-01-05 | 安徽美芝制冷设备有限公司 | Crankshaft for reciprocating compressor and reciprocating compressor provided with same |
| WO2018040351A1 (en) * | 2016-08-31 | 2018-03-08 | 安徽美芝制冷设备有限公司 | Crankshaft for reciprocating compressor and reciprocating compressor |
-
1984
- 1984-05-30 JP JP11042484A patent/JPS60256614A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS60256614A (en) | 1985-12-18 |
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