JPH09273619A - Connecting structure for driving shaft of hydraulic pump or the like and pulley - Google Patents
Connecting structure for driving shaft of hydraulic pump or the like and pulleyInfo
- Publication number
- JPH09273619A JPH09273619A JP10464596A JP10464596A JPH09273619A JP H09273619 A JPH09273619 A JP H09273619A JP 10464596 A JP10464596 A JP 10464596A JP 10464596 A JP10464596 A JP 10464596A JP H09273619 A JPH09273619 A JP H09273619A
- Authority
- JP
- Japan
- Prior art keywords
- pulley
- drive shaft
- shaft
- press
- driving 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
Landscapes
- Pulleys (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明は、油圧ポンプ等の
駆動軸とプーリの結合構造の改良に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement in a coupling structure of a drive shaft such as a hydraulic pump and a pulley.
【０００２】[0002]
【従来の技術】油圧ポンプの駆動軸とプーリの軸着部の
結合構造としては、例えば、図４に示す様な構造のもの
が実用されている。即ち、プーリ１は、所定の強度を有
する材料で所謂車輪状に形成され、外周側にベルト介装
部１Ａを有してなる一方で、中央部に油圧ポンプの駆動
軸２の先端側を圧入する軸着部１Ｂを有している。尚、
図示例にあって、外周にＶベルト（図示せず）を嵌装さ
せる複数本のＶ溝を有しているベルト介装部１Ａは、数
箇所のパンチ穴１Ｃにより肉抜きされたアーム１Ｄによ
り、軸着部１Ｂと一体的に成形される。2. Description of the Related Art As a coupling structure of a drive shaft of a hydraulic pump and a shaft mounting portion of a pulley, for example, a structure as shown in FIG. 4 has been put into practical use. That is, the pulley 1 is formed in a so-called wheel shape with a material having a predetermined strength, and has a belt interposition portion 1A on the outer peripheral side, while the front end side of the drive shaft 2 of the hydraulic pump is press-fitted in the central portion. It has a shaft mounting portion 1B. still,
In the illustrated example, the belt interposition part 1A having a plurality of V-grooves for fitting a V-belt (not shown) on the outer periphery is provided by the arm 1D thinned by several punch holes 1C. , And is integrally formed with the shaft attachment portion 1B.
【０００３】また、油圧ポンプの駆動軸２は、その後端
が油圧ポンプＰにおけるローター３への圧入等による連
結を可能にするように形成されている。それ故、上記プ
ーリ１は軸着部１Ｂに油圧ポンプＰから突出する駆動軸
２の先端側を圧入し、上記駆動軸２に一体的に結合され
ることになる。Further, the drive shaft 2 of the hydraulic pump is formed so that its rear end can be connected to the rotor 3 of the hydraulic pump P by press fitting or the like. Therefore, the pulley 1 is press-fitted into the shaft attachment portion 1B at the tip end side of the drive shaft 2 protruding from the hydraulic pump P, and is integrally connected to the drive shaft 2.
【０００４】上記した従来のプーリ１にあっては、プー
リの軸着部１Ｂに油圧ポンプＰから突出する駆動軸２の
先端側を圧入するのであるが、圧入部の結合力を確保す
るためには、プーリ１の軸着部内径と駆動軸２の先端側
外径の寸法精度が重要である。 ここで駆動軸２は、炭
素鋼（例えばＳ４５Ｃ）の冷間引き抜き材から加工され
調質した後、外径を研磨仕上げしているために寸法精度
は十分（例えば０〜−０．０１ｍｍ）であるが、プーリ
１の軸着部内径は、プレス加工による寸法精度（例えば
０〜＋０．３ｍｍ）では不十分であるため、軸着部内径
を切削或いはローラバニッシュしたりする所謂後加工を
加えて寸法精度を確保（例えば−０．０３６〜−０．０
６６ｍｍ）している。後加工はプレスメーカーとは別の
加工メーカーが担当する場合が多く、搬送等の物流費が
余分に必要となる。In the conventional pulley 1 described above, the tip end side of the drive shaft 2 protruding from the hydraulic pump P is press-fitted into the shaft mounting portion 1B of the pulley, but in order to secure the coupling force of the press-fitting portion. Is important for the dimensional accuracy of the inner diameter of the shaft attachment portion of the pulley 1 and the outer diameter of the drive shaft 2 on the tip side. Here, the drive shaft 2 has sufficient dimensional accuracy (for example, 0 to -0.01 mm) because the outer diameter is polished and finished after being processed and tempered from a cold drawn material of carbon steel (for example, S45C). However, since the inner diameter of the shaft-attaching portion of the pulley 1 is insufficient in dimensional accuracy (for example, 0 to +0.3 mm) by press working, so-called post-processing such as cutting the inner diameter of the shaft-attaching portion or roller burnishing is added. Ensure dimensional accuracy (for example, -0.036 to -0.0
66 mm). In many cases, post-processing is handled by a processing maker other than the press maker, and extra logistics costs such as transportation are required.
【０００５】上記の問題を避ける方法としては、プーリ
と駆動軸の圧入を諦め、図５に示す様に両者を溶接して
一体化することが考えられる。バラツキ範囲は、プーリ
の軸着部内径Ｄｒをプレス加工のまま使用する場合は前
記例の様に０〜＋０．３ｍｍ，駆動軸の外径Ｄｄについ
ては０〜−０．０１ｍｍであるので、プーリの軸着部内
径Ｄｒが最大のものに駆動軸の外径Ｄｄが最小のものを
組み合わせる場合には、最大で０．３１ｍｍの嵌合隙間
を生ずる。この場合両者は軸方向に移動自由であるの
で、溶接に際しては、両者の位置関係（図５のＺ）の確
保、嵌合隙間に起因する駆動軸に対するプーリの傾き及
び芯ずれを防止するため、両者を固定して溶接する精度
の良い溶接治具が必要となる。そのうえ例え溶接が上手
くできたとしても、プーリの駆動時には溶接部に嵌合隙
間に起因する曲げ荷重が加わるため、疲労破壊する恐れ
がある。As a method of avoiding the above problem, it is conceivable to give up the press-fitting of the pulley and the drive shaft, and weld them together as shown in FIG. The variation range is 0 to +0.3 mm as in the above example when the inner diameter Dr of the pulley shaft attachment portion is used as pressed, and the outer diameter Dd of the drive shaft is 0 to -0.01 mm. When a shaft mounting portion having the largest inner diameter Dr is combined with a drive shaft having the smallest outer diameter Dd, a maximum fitting gap of 0.31 mm is generated. In this case, since both are free to move in the axial direction, at the time of welding, in order to secure the positional relationship between them (Z in FIG. 5) and prevent the pulley from tilting and deviating from the drive shaft due to the fitting gap, It is necessary to have a welding jig with high precision that fixes and welds both. Moreover, even if the welding is successful, a bending load due to the fitting gap is applied to the welded portion when the pulley is driven, which may cause fatigue failure.
【０００６】[0006]
【発明が解決しようとする課題】この発明は、上記した
事情に鑑みて創案されたものであって、その目的とする
ところは、プーリの軸着部内径がプレス加工されたまま
でも、十分な結合力が確保できるプーリと駆動軸の結合
構造を提供することである。SUMMARY OF THE INVENTION The present invention was created in view of the above-mentioned circumstances, and its object is to achieve a sufficient result even if the inner diameter of the shaft-attaching portion of the pulley remains pressed. It is an object of the present invention to provide a connecting structure of a pulley and a drive shaft capable of ensuring a connecting force.
【０００７】[0007]
【課題を解決するための手段】以上の課題を解決するた
めに本発明の採った手段は、「外周側がベルト介装部と
されるとともに中央部が軸着部とされるプーリに駆動軸
を圧入する結合構造において、駆動軸の先端側に先端の
外径が駆動軸の外径に対して小となるテーパ部を形成
し、前記プーリの軸着部に当該テーパ部を圧入して係止
するとともに、駆動軸の先端側外周をプーリの軸着部に
補強溶接したこと」である。そして上記プーリの軸着部
は、内径が一定の円筒状或いはテーパ状に形成される。[Means for Solving the Problems] In order to solve the above problems, the means adopted by the present invention is that "a drive shaft is attached to a pulley whose outer peripheral side is a belt interposition part and whose central part is a shaft mounting part. In the press-fitting coupling structure, a taper portion is formed on the tip side of the drive shaft such that the outer diameter of the tip is smaller than the outer diameter of the drive shaft, and the taper portion is press-fitted and locked to the shaft attachment portion of the pulley. At the same time, the outer periphery of the drive shaft on the tip side was reinforced and welded to the shaft attachment part of the pulley. " The shaft attachment portion of the pulley is formed in a cylindrical shape or a tapered shape with a constant inner diameter.
【０００８】[0008]
【発明の実施の形態】次に本発明に係る油圧ポンプの駆
動軸とプーリの軸着部の結合構造を図１に示す第１実施
形態に基づき、従来技術と同一部分には同一符号を付し
て説明する。まず炭素鋼（例えばＳ４５Ｃ）の冷間引き
抜き材から加工された駆動軸１０２の先端側に先端の外
径Ｄｕが駆動軸の本体側１０２Ａの外径Ｄｄに対して小
（Ｄｕ＜Ｄｄ）となるテーパ部１０２Ｂを形成する。先
端の外径Ｄｕはプーリの軸着部内径Ｄｐより小さくする
ことにより、係合初期の挿入を容易にすることができ
る。BEST MODE FOR CARRYING OUT THE INVENTION Next, based on the first embodiment shown in FIG. 1 which shows the coupling structure of a drive shaft of a hydraulic pump and a shaft mounting portion of a pulley according to the present invention, the same parts as those in the prior art are designated by the same reference numerals. And explain. First, the outer diameter Du of the tip of the drive shaft 102 machined from a cold drawn material of carbon steel (for example, S45C) is smaller (Du <Dd) than the outer diameter Dd of the drive shaft main body side 102A. The tapered portion 102B is formed. By making the outer diameter Du of the tip smaller than the inner diameter Dp of the shaft-attaching portion of the pulley, insertion at the initial stage of engagement can be facilitated.
【０００９】駆動軸の本体側１０２Ａの外径Ｄｄ及び先
端側の補強溶接Ｗ部を除くテーパ部１０２Ｂには、必要
に応じて高周波焼き入れ等を実施することによりプーリ
をＶベルトで駆動する際に駆動軸に加わる曲げモーメン
トに対する耐久性を向上させることができる。駆動軸に
加わる曲げモーメントはプーリの軸着部の挿入側で最大
となるので、曲げモーメントの小さい先端側の補強溶接
部には高周波焼き入れ等の必要がなく、高周波焼き入れ
部の溶接に伴う障害をなくすることができる。When the outer diameter Dd of the main body side 102A of the drive shaft and the tapered portion 102B except the reinforcing welding W portion on the tip side are subjected to induction hardening or the like as required, the pulley is driven by the V belt. The durability against the bending moment applied to the drive shaft can be improved. Since the bending moment applied to the drive shaft is maximum on the insertion side of the pulley shaft attachment part, there is no need for induction hardening at the tip side of the reinforcement welding part where the bending moment is small. The obstacles can be eliminated.
【００１０】圧延鋼板（例えばＳＰＨ３）からプレス成
形されたプーリの軸着部１０１Ｂは、駆動軸１０２が硬
い材質（例えばＳ４５Ｃ）であるため、前記テーパ部１
０２Ｂと係合開始後は、前記プーリの軸着部１０１Ｂの
円筒部内径Ｄｐがテーパ部１０２Ｂにより弾性変形を受
けながら一体的に結合され、図１（Ａ）のＺで示す先端
位置迄圧入される。この場合にはテーパ部との係合長が
短い圧入初期には比較的小さな圧入荷重となり、テーパ
部１０２Ｂとの係合長が増大するに従い圧入荷重も増え
て、先端位置Ｚ迄圧入されたとき最大圧入荷重となる。Since the drive shaft 102 is made of a hard material (for example, S45C), the shaft-attaching portion 101B of the pulley press-formed from the rolled steel plate (for example, SPH3) has the tapered portion 1
After the engagement with 02B is started, the inner diameter Dp of the cylindrical portion of the shaft mounting portion 101B of the pulley is integrally coupled while being elastically deformed by the tapered portion 102B, and is press-fitted to the tip position indicated by Z in FIG. 1 (A). It In this case, when the engagement length with the taper portion is short, the press-fitting load is relatively small in the initial stage of press-fitting, and as the engagement length with the taper portion 102B increases, the press-fitting load also increases, and when the press-fitting is performed to the tip position Z. Maximum press-fit load.
【００１１】上記駆動軸１０２のプーリの軸着部１０１
Ｂへの結合に際しては、図３に示す様にプーリ１０１を
基台Ｅに水平に保持し、駆動軸１０２の先端側のテーパ
部１０２Ｂを圧入治具Ｊにより垂直方向に押し下げ、プ
ーリの軸着部１０１Ｂに圧入する。圧入治具Ｊは、基台
Ｅに水平に保持されたプーリ１０１の軸着部内径に同芯
状に配置された図示しない押圧シリンダ等に基端部が結
合され、プーリ１０１に対して上下動自在に駆動される
ものである。Shaft mounting portion 101 of the pulley of the drive shaft 102
At the time of coupling to B, the pulley 101 is held horizontally on the base E as shown in FIG. 3, and the taper portion 102B on the tip side of the drive shaft 102 is pushed down vertically by the press-fitting jig J to attach the pulley shaft. Press-fit into the part 101B. The press-fitting jig J has a base end coupled to a pressing cylinder (not shown) arranged concentrically with the inner diameter of the shaft-attaching portion of the pulley 101 held horizontally on the base E, and moves vertically with respect to the pulley 101. It can be driven freely.
【００１２】この場合テーパ部の形状は図１（Ｃ）に示
す如く、駆動軸の先端の外径Ｄｕがプーリの軸着部内径
Ｄｐより小であるので、テーパ部１０２Ｂの本体側の外
径Ｄｄが大きくても相手部材を変形させながら結合する
ことができる。圧入代（Ｄｄ−Ｄｐ）を適正に設定する
ことにより、プーリの軸着部内径寸法がプレス成形のま
まの比較的広い範囲（例えば０〜＋０．３ｍｍ）にバラ
ついていても所定の結合強度を得ることができる。両者
は圧入嵌合であるから、圧入時に両者の位置関係（図１
のＺ）の確保、駆動軸に対するプーリの傾き及び芯ずれ
を防止することは容易で、圧入完了後もその状態を保持
することができる。テーパ部１０２Ｂはプーリの軸着部
に対する適正な結合力と安定した保持機能を発生させる
のが目的であるから、本例に示した直線状に限らず、例
えばなだらかな円弧状であっても差支えない。In this case, as shown in FIG. 1C, since the outer diameter Du of the tip of the drive shaft is smaller than the inner diameter Dp of the shaft bearing portion of the pulley, the outer diameter of the tapered portion 102B on the main body side is as shown in FIG. Even if Dd is large, the mating member can be coupled while being deformed. By properly setting the press-fitting margin (Dd-Dp), the predetermined coupling strength can be obtained even if the inner diameter of the shaft-attaching part of the pulley varies in a relatively wide range (for example, 0 to +0.3 mm) as it is in press molding. Obtainable. Since both are press-fitted, the positional relationship between them when press-fitting (Fig. 1
Z), the inclination of the pulley with respect to the drive shaft, and the prevention of misalignment can be easily maintained, and the state can be maintained even after the press-fitting is completed. The purpose of the tapered portion 102B is to generate an appropriate coupling force with respect to the shaft-attaching portion of the pulley and a stable holding function. Therefore, the tapered portion 102B is not limited to the linear shape shown in this example, but may be a gentle arc shape. Absent.
【００１３】プーリ１０１は、外側のベルト介装部１０
１Ａを介してエンジン等の駆動トルクを駆動軸に伝達す
るのであるが、テーパ部１０２Ｂはプーリの軸着部内径
Ｄｐを変形させて、しっかりと結合しているため、大き
な駆動トルクを伝えることができる。両者は図１（Ａ）
に示すＺの位置迄圧入した後、駆動軸の先端側外周をプ
ーリの軸着部に周上数ヶ所のスポット溶接又は全周溶接
をする所謂補強溶接Ｗを実施することによって、結合強
度を確実にものとする。両者の位置関係（図１のＺ）多
少ずれても良い場合には、圧入作業を圧入荷重で管理す
ることができるので、補強溶接前の結合強度が安定す
る。The pulley 101 has an outer belt interposed portion 10
The drive torque of the engine or the like is transmitted to the drive shaft via 1A, but since the tapered portion 102B deforms the inner diameter Dp of the shaft attachment portion of the pulley and is firmly coupled, it is possible to transmit a large drive torque. it can. Both are shown in Figure 1 (A)
After press-fitting to the Z position shown in Fig. 2, by performing so-called reinforced welding W in which the outer periphery of the tip end side of the drive shaft is spot-welded or all-around welded to the shaft attachment part of the pulley at several places on the circumference, the bond strength is secured It is assumed that When the positional relationship between the two (Z in FIG. 1) may be slightly deviated, the press-fitting work can be controlled by the press-fitting load, so that the bonding strength before reinforcement welding is stable.
【００１４】圧入作業を両者の位置関係（図１のＺ）で
管理する場合には、プーリの軸着部内径Ｄｐのバラツキ
により圧入荷重も変動するが、プーリの軸着部内径の挿
入側は、少なくとも駆動軸のテーパ部１０２Ｂに対して
圧入となる様な寸法設定が可能であり、図５の場合とは
異なり圧入後挿入側には隙間がないので、補強溶接部に
は曲げ荷重が加わることはないため、図５の場合の様な
疲労破壊の恐れがない。 また通常の駆動状態において
は、駆動軸に対するプーリ軸着部の離脱力は殆ど作用し
ないので、補強溶接Ｗは簡単なもので良い。When the press-fitting work is controlled by the positional relationship between them (Z in FIG. 1), the press-fitting load also fluctuates due to the variation in the inner diameter Dp of the shaft-attaching portion of the pulley, but the insertion side of the inner diameter of the shaft-attaching portion of the pulley is The size of the drive shaft can be press-fitted into at least the tapered portion 102B, and unlike the case of FIG. 5, there is no gap on the insertion side after press-fitting, so a bending load is applied to the reinforcing welded portion. Therefore, there is no fear of fatigue failure as in the case of FIG. Further, in a normal driving state, since the detaching force of the pulley shaft attaching portion with respect to the drive shaft hardly acts, the reinforcement welding W may be simple.
【００１５】図２に示す結合構造は、プーリと駆動軸の
結合に係る第２実施形態を示すものである。第１実施形
態との相違点は、プーリ２０１の軸着部内径をアーム２
０１Ｄが立ち上がる基端側の外径Ｄｗが挿入側の外径Ｄ
ｖよりも小（Ｄｗ＜Ｄｖ）となるテーパ状に形成したこ
とである。この場合には軸着部内径のプレス成形性が、
良くなることもあって、寸法のバラツキを小さくするこ
とができる。そのうえ駆動軸のテーパと軸着部内径のテ
ーパとを適正に設定することにより、係合長が短い圧入
初期から所定位置Ｚ迄の圧入荷重の増加割合を、自由に
設定できるので、圧入作業を圧入荷重で管理する場合の
作業が比較的容易になる。補強溶接Ｗについては前述の
第１実施形態と同様であるので説明を省略する。The coupling structure shown in FIG. 2 shows a second embodiment relating to the coupling between the pulley and the drive shaft. The difference from the first embodiment is that the inner diameter of the shaft attachment portion of the pulley 201 is set to the arm 2
The outer diameter Dw on the base end side where 01D rises is the outer diameter D on the insertion side
That is, the taper shape is smaller than v (Dw <Dv). In this case, the press formability of the inner diameter of the shaft attachment part,
In some cases, it is possible to improve the quality, and it is possible to reduce the dimensional variation. Moreover, by appropriately setting the taper of the drive shaft and the taper of the inner diameter of the shaft-attaching portion, the increase rate of the press-fitting load from the initial press-fitting with a short engagement length to the predetermined position Z can be freely set. The work for controlling by press-fitting load becomes relatively easy. The reinforcement welding W is the same as that in the first embodiment described above, and therefore its description is omitted.
【００１６】[0016]
【発明の効果】以上詳述した通り、本発明においては、
上記実施形態にて例示した如く、プーリの軸着部に駆動
軸のテーパ部を所定の保持力を持たせて圧入し、更に駆
動軸の先端側外周をプーリの軸着部に補強溶接を実施し
て軸方向の移動を防止するとともに、両者の結合強度を
確実なものとする係止構造であるため、従来例に見られ
たような圧入条件が厳しいことに伴うプーリの単一部品
段階での後加工を廃止することができる。また、テーパ
部の寸法及び形状管理さえ十分に行えば、プレス成形さ
れたプーリの軸着部内径のバラツキが多少大きくても、
駆動軸のテーパ部がプーリの軸着部内径を変形させて係
合したうえ、更に補強溶接を実施するため十分な結合力
が保証されるので、品質の安定化が容易であるととも
に、不良品の発生が防止されることにより製造コストを
低減することができる。更にプーリの軸着部内径をテー
パ状にして成形性を改善した場合には、軸着部内径寸法
のバラツキが減少し、補強溶接前の結合強度を安定化す
ることができる。As described in detail above, in the present invention,
As exemplified in the above embodiment, the taper portion of the drive shaft is press-fitted into the shaft attachment portion of the pulley with a predetermined holding force, and further the outer periphery of the tip end side of the drive shaft is reinforced and welded to the shaft attachment portion of the pulley. This prevents the movement in the axial direction and secures the coupling strength between the two.Therefore, in the single component stage of the pulley due to the severe press-fitting conditions seen in the conventional example. Post-processing can be abolished. In addition, if the dimensions and shape of the tapered portion are sufficiently managed, even if the variation in the inner diameter of the shaft-attached portion of the press-molded pulley is somewhat large,
The tapered part of the drive shaft deforms and engages the inner diameter of the shaft bearing part of the pulley, and since the reinforcement welding is performed, a sufficient coupling force is guaranteed, so quality stabilization is easy and defective products The production cost can be reduced by preventing the occurrence of. Further, when the inner diameter of the shaft-attaching portion of the pulley is tapered to improve the formability, the variation in the inner diameter of the shaft-attaching portion is reduced, and the bonding strength before the reinforcement welding can be stabilized.
【図１】（Ａ）本発明の第１実施形態に係るプーリと駆
動軸の結合状態を示す断面図である。 （Ｂ）第１実施形態に係るプーリの軸着部の要部断図面
である。 （Ｃ）第１実施形態に係る駆動軸のテーパ部の形状を示
す図面である。FIG. 1A is a cross-sectional view showing a coupled state of a pulley and a drive shaft according to a first embodiment of the present invention. (B) It is a fragmentary drawing of a shaft attachment portion of the pulley according to the first embodiment. (C) It is drawing which shows the shape of the taper part of the drive shaft which concerns on 1st Embodiment.
【図２】（Ａ）本発明の第２実施形態に係るプーリと駆
動軸の結合状態を示す断面図である。 （Ｂ）第２実施形態に係るプーリの軸着部の要部断図面
である。 （Ｃ）第２実施形態に係る駆動軸のテーパ部の形状を示
す図面である。FIG. 2A is a sectional view showing a coupled state of a pulley and a drive shaft according to a second embodiment of the present invention. (B) It is a fragmentary drawing of a shaft attachment portion of a pulley according to a second embodiment. (C) It is drawing which shows the shape of the taper part of the drive shaft which concerns on 2nd Embodiment.
【図３】 従来技術に係るプーリと駆動軸の結合状
態を示す断面図である。FIG. 3 is a cross-sectional view showing a coupled state of a pulley and a drive shaft according to a conventional technique.
Ｄｕ 駆動軸先端の外径 Ｄｄ 駆動軸の外径 １，１０１，２０１ プーリ １Ａ，１０１Ａ ベルト介装部 １０１Ｂ，２０１Ｂ プーリの軸着部 １０２ 駆動軸 １０２Ｂ テーパ部 Du Drive shaft outer diameter Dd Drive shaft outer diameter 1,101,201 Pulleys 1A, 101A Belt interposition part 101B, 201B Pulley shaft attachment part 102 Drive shaft 102B Tapered part
【手続補正書】[Procedure amendment]
【提出日】平成８年８月２１日[Submission date] August 21, 1996
【手続補正１】[Procedure amendment 1]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】図面の簡単な説明[Correction target item name] Brief description of drawings
【補正方法】追加[Correction method] Added
【補正内容】[Correction contents]
【図面の簡単な説明】[Brief description of drawings]
【図１】 （Ａ）本発明の第１実施形態に係るプーリと
駆動軸の結合状態を示す断面図である。 （Ｂ）第１実施形態に係るプーリの軸着部の要部断面図
である。 （Ｃ）第１実施形態に係る駆動軸のテーパ部の形状を示
す図面である。FIG. 1A is a cross-sectional view showing a coupled state of a pulley and a drive shaft according to a first embodiment of the present invention. (B) It is a cross-sectional view of a main part of a shaft attachment portion of the pulley according to the first embodiment. (C) It is drawing which shows the shape of the taper part of the drive shaft which concerns on 1st Embodiment.
【図２】 （Ａ）本発明の第２実施形態に係るプーリと
駆動軸の結合状態を示す断面図である。 （Ｂ）第２実施形態に係るプーリの軸着部の要部断面図
である。 （Ｃ）第２実施形態に係る駆動軸のテーパ部の形状を示
す図面である。FIG. 2 (A) is a sectional view showing a coupled state of a pulley and a drive shaft according to a second embodiment of the present invention. (B) It is a cross-sectional view of a main part of a shaft attachment portion of the pulley according to the second embodiment. (C) It is drawing which shows the shape of the taper part of the drive shaft which concerns on 2nd Embodiment.
【図３】従来技術に係るプーリと駆動軸の結合状態を示
す断面図である。FIG. 3 is a cross-sectional view showing a connected state of a pulley and a drive shaft according to a conventional technique.
【図４】従来技術に係る油圧ポンプとプーリの結合状態
を示す断面図である。FIG. 4 is a cross-sectional view showing a connected state of a hydraulic pump and a pulley according to a conventional technique.
【図５】従来技術に係るプーリと駆動軸の溶接結合状態
を示す断面図である。FIG. 5 is a sectional view showing a welded state of a pulley and a drive shaft according to a conventional technique.
【符号の説明】 Ｄｕ 駆動軸先端の外径 Ｄｄ 駆動軸の外径 １，１０１，２０１ プーリ １Ａ， １０１Ａ ベルト介装部 １０１Ｂ，２０１Ｂ プーリの軸着部 １０２ 駆動軸 １０２Ｂ テーパ部 Ｗ 補強溶接 ＤＰ 一定であるプーリの軸着部内径 Ｄｖ プーリの挿入側軸着部内径 Ｄｗ プーの基端側軸着部内径[Explanation of Codes] Du Outer diameter of drive shaft tip Dd Outer diameter of drive shaft 1,101,201 Pulleys 1A, 101A Belt interposition part 101B, 201B Pulley shaft attachment part 102 Drive shaft 102B Tapered part W Reinforcement welding DP Constant Is the inner diameter of the shaft attachment part of the pulley Dv is the inner diameter of the shaft attachment part of the pulley Dw is the inner diameter of the proximal end of the pulley
Claims (3)
中央部が軸着部とされるプーリに駆動軸を圧入する結合
構造において、駆動軸の先端側に先端の外径が駆動軸の
外径に対して小となるテーパ部を形成し、前記プーリの
軸着部に当該テーパ部を圧入して係止するとともに、駆
動軸の先端側外周をプーリの軸着部に補強溶接したこと
を特徴とする駆動軸とプーリの結合構造。1. In a coupling structure in which a drive shaft is press-fitted into a pulley whose outer peripheral side is a belt interposition part and whose central part is a shaft mounting part, the outer diameter of the front end is the outer side of the drive shaft. A taper portion that is smaller than the diameter is formed, and the taper portion is press-fitted and locked in the shaft attachment portion of the pulley, and the outer periphery of the tip end side of the drive shaft is reinforced and welded to the pulley shaft attachment portion. Characteristic drive shaft and pulley coupling structure.
特徴とする請求項１に記載の駆動軸とプーリの結合構
造。2. The drive shaft / pulley coupling structure according to claim 1, wherein the inner diameter of the shaft attachment portion of the pulley is constant.
対して大となるテーパ状に形成したことを特徴とする請
求項１に記載の駆動軸とプーリの結合構造。3. The drive shaft-pulley coupling structure according to claim 1, wherein the inner diameter of the shaft attachment portion of the pulley is formed such that the insertion side is larger than the base end side.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10464596A JPH09273619A (en) | 1996-04-01 | 1996-04-01 | Connecting structure for driving shaft of hydraulic pump or the like and pulley |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10464596A JPH09273619A (en) | 1996-04-01 | 1996-04-01 | Connecting structure for driving shaft of hydraulic pump or the like and pulley |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH09273619A true JPH09273619A (en) | 1997-10-21 |
Family
ID=14386203
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10464596A Pending JPH09273619A (en) | 1996-04-01 | 1996-04-01 | Connecting structure for driving shaft of hydraulic pump or the like and pulley |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH09273619A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002276776A (en) * | 2001-03-15 | 2002-09-25 | Denso Corp | Power transmitting device |
-
1996
- 1996-04-01 JP JP10464596A patent/JPH09273619A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002276776A (en) * | 2001-03-15 | 2002-09-25 | Denso Corp | Power transmitting device |
| JP4617584B2 (en) * | 2001-03-15 | 2011-01-26 | 株式会社デンソー | Power transmission device |
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