JP4154035B2 - Shaft coupling - Google Patents

Shaft coupling Download PDF

Info

Publication number
JP4154035B2
JP4154035B2 JP19750798A JP19750798A JP4154035B2 JP 4154035 B2 JP4154035 B2 JP 4154035B2 JP 19750798 A JP19750798 A JP 19750798A JP 19750798 A JP19750798 A JP 19750798A JP 4154035 B2 JP4154035 B2 JP 4154035B2
Authority
JP
Japan
Prior art keywords
joint
jaw
joint part
shaft coupling
jaws
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 - Fee Related
Application number
JP19750798A
Other languages
Japanese (ja)
Other versions
JPH1172122A (en
Inventor
ゲルバー クリスティアン
マイアー トーマス
ケラー シュテファン
Original Assignee
シンテイラ アクチエンゲゼルシヤフト
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 シンテイラ アクチエンゲゼルシヤフト filed Critical シンテイラ アクチエンゲゼルシヤフト
Publication of JPH1172122A publication Critical patent/JPH1172122A/en
Application granted granted Critical
Publication of JP4154035B2 publication Critical patent/JP4154035B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/001—Gearings, speed selectors, clutches or the like specially adapted for rotary tools
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • F16D3/12—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted for accumulation of energy to absorb shocks or vibration
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/80—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive in which a fluid is used
    • 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
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Vibration Prevention Devices (AREA)
  • Mechanical Operated Clutches (AREA)
  • Catching Or Destruction (AREA)
  • Gripping On Spindles (AREA)
  • Jigs For Machine Tools (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は、原動機、特に手持ち式電動工作機械のための軸継手であって、継手ジョーを支持している第１の継手部分を有していて、この第１の継手部分が駆動軸と相対回動不能に（一緒に回転するように）結合されており、さらに継手ジョーを支持している第２の継手部分を有していて、この第２の継手部分が被駆動軸と相対回動不能に（一緒に回転するように）結合され、第２の継手部分の継手ジョーが第１の継手部分の継手ジョーの間に回転用の遊びを伴って位置している形式のものに関する。
【０００２】
このような軸継手は、ねじ回し、穴あけ機などの手持ち式電動工作機械に応用される。
【０００３】
【従来の技術】
このような軸継手を有する公知の電動ねじ回し（合衆国特許第５０１６５０１号明細書）では、ねじ工具のための工具保持部が被駆動軸と相対回動不能に結合しており、駆動軸は可逆電動機によって駆動されている。そうすることによって、ねじ工具は右回りと左回りに駆動され得る。つまりねじを締めたり緩めたりできる。
【０００４】
被駆動軸と結合している継手部分と転動体を介して連通している外側保持リングを設けることによって、被駆動軸と結合している継手部分がねじ回しハウジングに固持され得るので、電動ねじ回しは手動ねじ回しとして用いることができる。
【０００５】
軸継手内で両継手部分の継手ジョーの間に回転用の遊びが存在している結果として、負荷交替時には継手部分が相互に当接することによって大きい騒音が形成される。さらに、無負荷運転中に振動が発生し、それに伴い同様にぼ妨害雑音が生じる。
【０００６】
【発明が解決しようとする課題】
本発明の課題は、上記従来技術における欠点を取り除くことである。
【０００７】
【課題を解決するための手段】
上記の課題を解決するために本発明の構成では、第１の継手部分と第２の継手部分との間に、両継手部分の相対回動を互いに制動する減衰装置が配置されており、減衰装置が、両継手部分の相対回動時に摩擦モーメントを生み出す摩擦部材を有しており、摩擦部材が、両継手部分の共軸面上に挿入されている少なくとも１つのスプリングワイヤによって形成されている。
【０００８】
【発明の効果】
以上のような特徴を有する本発明による軸継手は、継手部分の相対回動時に作用する減衰装置によって、継手部分の交替サイクルが制動されて行われるという利点を有している。
【０００９】
この場合、減衰装置は、減衰モーメントが一定であるか、両継手部分の角速度差に直接比例するように設計され得る。そうすることにより、第１に、負荷交替が小さい場合、つまり両継手部分のトルク差が小さい場合は、互いに接触する継手ジョーにおける衝止面の変位が防止され、第２に、トルク差が比較的大きい場合はエネルギー変換によって衝撃が減衰される。
【００１０】
そうすることによって、従来発生していた不都合な運転騒音は抑圧され、本発明の継手を装備された手持ち式電動工作機械は、騒音がわずかで、振動がなく、交替サイクルによるいわゆる惰性効果がないので品質感が著しく高められる。継手部分は発生するわずかな数の衝突や衝撃によって負荷されるにすぎず、しかもこれらの衝突や衝撃も減衰されて弱いので、継手の耐久時間が高められる。
【００１１】
請求項２以下に記載の方策により、本発明の軸継手の有利な構成および改良が可能である。
【００１２】
本発明の好ましい実施例に従い、減衰装置は、両継手部分の相対回動時に摩擦モーメントを生み出す摩擦部材を有している。この摩擦部材は、両継手部分の共軸面の間に挿入されている少なくとも１つのスプリングワイヤによって形成されている。少なくとも２つのスプリングワイヤが設けられていて、それぞれＵ字形スプリングクリップの脚部を形成しており、両脚部が、一方の継手部分の共軸面に形成された軸方向スリットまたは軸方向溝内に回転方向に移動しないように挿入されていて、他方の継手部分の共軸面に当接している。
【００１３】
この場合、スプリングクリップの脚部を保持するための両軸方向スリットは、共軸面上に直径方向または割線方向に配置されてよい。このような構造で形成することによって、減衰装置の製造コストは極めてわずかである。材料コストは、Ｕ字形スプリングクリップと、スプリングクリップが簡単に挿入される一方の継手部分の保持溝に限られている。材料コストが減らされているために、組立コストはわずかである。
【００１４】
【発明の実施の形態】
以下に、本発明の実施例を図面に基づいて詳細に説明する。
【００１５】
図１と図２に示された、手持ち式電動工作機械、特に電動穴あけ機または電動ねじ回しのための軸継手は、継手ジョーによって互いに係合する第１の継手部分１１と第２の継手部分１２を有している。第１の継手部分１１は、可逆電動機の駆動軸（図示しない）と相対回動不能に（一緒に回転するように）結合されているが、第２の継手部分１２は、ねじ回しまたは穴あけ機を固定するための工具保持部と連結している被駆動軸１３と結合されている。
【００１６】
第１の継手部分１１は、基体１１３から軸方向に突出している２対の継手ジョーを支持している。この場合、一方のジョー対の継手ジョー１１１は同一に形成されていて、継手部分１１で互いに向き合っており、第２のジョー対の継手ジョー１１２も同様に同一に形成されていて、継手部分１１でやはり互いに向き合っているが、第１のジョー対の継手ジョー１１１に対して約７５度の円周角だけずれている。
【００１７】
第２の継手部分１２は、基体１２２から半径方向に突き出している２つの継手ジョー１２１を支持している。これらの継手ジョー１２１は、組み立てられた継手においてそれぞれ１つの継手ジョー１２１が第１の継手部分１１の継手ジョー１１１と１１２との間に回転用の遊びを伴って位置しているように、第２の継手部分１２に配置されている。
【００１８】
各々の継手ジョー１１１は半径方向連行面１１１ａを有している。この連行面１１１ａは継手ジョー１２１に形成された半径方向衝止面１２１ａと協働して、第２の継手部分１２を図１で時計と反対方向に回転連行する。同様に、各々の継手ジョー１１２は半径方向連行面１１２ａを有している。この連行面１１２ａは継手ジョー１２１に形成された半径方向衝止面１２１ｂと協働して、第２の継手部分１２を時計方向に回転連行する。
【００１９】
継手ジョー１１１および１１２は、内側の共軸の円弧状のジョー面１１１ｃもしくは１１２ｃで、第２の継手部分１２の基体１２２の継手ジョー１２１の間に延びている共軸基体面１２２ｃに滑り遊びを有して当接している。
【００２０】
第１の継手部分１１が駆動軸を介して図１で時計と反対方向に駆動されると、継手ジョー１１１はそれらの連行面１１１ａで継手ジョー１２１の衝止面１２１ａに当接し、継手部分１２を回転方向に連行する。これに対し、図１で継手部分１１が時計方向に回転すると、継手ジョー１１２はそれらの半径方向連行面１１２ａで継手ジョー１２１の衝止面１２１ｂに当接し、回転時に第２の継手部分１２を連行する。
【００２１】
負荷交替時に連行面１１１ａもしくは１１２ａが衝止面１２１ａおよび１２１ｂに当たることによって発生する騒音を低減するために、両継手部分の相対回動を互いに制動する減衰装置１４が両継手部分の間に設けられている。図１および図２の実施例において、減衰装置１４は継手部分１１、１２の相対回動時に摩擦モーメントを生み出す摩擦部材を有している。
【００２２】
摩擦部材はここでは、２つのスプリングワイヤによって形成されており、これらはＵ字形スプリングクリップ１５の脚部１５１および１５２を形成している（図２）。クリップの両脚部１５１、１５２は、第２の継手部分１２の基体１２２の共軸面１２２ｃに設けられた軸方向スリットまたは軸方向溝１６、１７内に位置している。この場合、両脚部１５１、１５２は、軸方向溝１６、１７内に回転方向で移動しないように保持されていて、第１の継手部分１１の両継手ジョー１１１の共軸面１１１ｃに当接している。
【００２３】
しかし、基体の共軸面１２２ｃおよび継手ジョー１１１ｃの共軸面上に挿入されているスプリングワイヤの数は増やすことも、最小限１個とすることもできる。スプリングワイヤもしくは両クリップ脚部１５１、１５２は負荷交替時に両継手部分１１と１２との間に摩擦モーメントを生み出す。この摩擦モーメントは、第１に、両継手部分１１と１２との間のトルク差が小さい場合には両継手部分１１、１２の変位を妨げ、第２に、両継手部分１１と１２との間のトルク差が比較的大きい場合には回転エネルギーから熱へのエネルギー変換によって、継手ジョー１１、１２が互いに当たる際の衝撃を著しく減衰する。
【００２４】
工具交換のために、被駆動軸１３と結合した第２の継手部分１２は、手持ち式電動工作機械の機械ハウジングに固定され得る。この目的のために、機械ハウジングに回転可能に配置された保持リング１８が設けられている。保持リング１８は両継手部分１１、１２に対して共軸に配置され、互いに係合する継手ジョー１１１、１１２を取り囲んでいる。
【００２５】
保持リング１８と第２の継手部分１２との間には締付け体１９が配置されている。これらの締付け体１９は、保持リング１８の回動時に当該保持リング１８を第２の継手部分１２と共に締め付ける。図１と図２に示す実施例では、締付け体１９は転動体２０、たとえばシリンダ、球またはローラとして形成されている。
【００２６】
これらの転動体は一方では保持リング１８の内側リング面１８１に支えられており、他方では第２の継手部分１２の基体１２２における接線方向の面区分１２２ｄで当該面区分１２２ｄのほぼ中心に支えられている。この場合、それぞれ１つの転動体２０が第１の継手部分１１の継手ジョー１１１と１１２との間に回転用の遊びを伴って挿入されている。
【００２７】
接線方向の面区分１２２ｄは第２の継手部分１２の基体１２２における共軸面１２２ｃに斜角面又は扁平面取り面を設けることによって形成されており、両継手ジョー１２１の間の中心に位置している。
【００２８】
各々の転動体２０と当該転動体２０に向けられた第１の継手部分１１における継手ジョー１１１および１１２の半径方向連行面１１ｂおよび１１２ｂとの間隔は、次のように寸法設定されている。すなわち、第１の継手部分１１の一方の継手ジョー１１１もしくは１１２が第２の継手部分１２の継手ジョー１２１に当接して一方又は他方の回転方向で回転連行すると、第１の継手部分１１の他方の継手ジョー１１２もしくは１１１の半径方向連行面１１２ｂもしくは１１１ｂが転動体２０に当接してこれを回転連行する。
【００２９】
第１の継手部分１１が図１で時計と反対方向に回転すると、両転動体２０は両継手ジョー１１２における半径方向連行面１１２ｂによって回転方向に連行され、その際に接線方向の面区分１２２ｄの内部におけるそれらの相対的位置を維持する。第１の継手部分１１が時計方向に回転すると、両転動体２０は両継手ジョー１１１における半径方向連行面１１１ｂによって回転方向に連行され、同様に接線方向の面区分１２２ｄの内部におけるほぼ中心位置を維持する。これにより、転動体２０は接線方向の面区分１２２ｄおよび保持リング１８の内側リング面１８１に沿って転動する。
【００３０】
これに対し、保持リング１８が一方の回転方向または他方の回転方向で両継手部分１１、１２に対して相対的に回動されると、転動体２０が変位して、第２の継手部分１２の接線方向の面区分１２２ｄと、保持リング１８の内側リング面１８１との間で締め付けられる。これにより、第２の継手部分１２は保持リング１８に回転不能に固持されるので、手持ち式電動工作機械の工具保持部と結合している第２の継手部分１２が機械ハウジングに固持されており、これにより工具保持部における工具交換が、たとえば既存の急速着脱ドリルチャックを用いて行われ得る。
【００３１】
電動ねじ回しとして形成された手持ち式電動工作機械では、第２の継手部分１２を機械ハウジングに固持することによって、電動ねじ回しは手動ねじ回しとしても用いることができる。
【００３２】
本発明は上記の実施例に制限されるものではない。たとえば両継手部分１１と１２との間の相対回動を制動するための減衰装置は、越流路によって互いに連通している、両継手部分１１と１２との間の液体が充填された容積可変の隙間によっても実現され得る。これにより、負荷交替時に液体が一方の隙間から越流路を通って他方の隙間に押しのけられ、それによって減衰作用が達成される。しかし、技術的コストはスプリングクリップ１５によって形成された減衰装置１４に比べてはるかに大きい。
【図面の簡単な説明】
【図１】本発明による手持ち式電動工作機械の軸継手の正面図である。
【図２】図１に示した軸継手の展開図である。
【符号の説明】
１１ 継手部分、 １２ 継手部分、 １３ 被駆動軸、 １４ 減衰装置、１５ 摩擦部材、 １６ 軸方向スリット、 １７ 軸方向溝、 １８ 保持リング、 １９ 締付け体、 ２０ 転動体、 １１１ 継手ジョー、 １１１ｂ 連行面、 １１２ 継手ジョー、 １１２ｂ 連行面、 １１１ｃ 共軸面、 １２１ 継手ジョー、 １２２ 基体、 １２２ｃ 共軸面、 １２２ｄ 面区分、 １５１ 脚部、 １５２ 脚部、 １８１ 内側リング面[0001]
BACKGROUND OF THE INVENTION
The present invention is a shaft coupling for a prime mover, particularly a hand-held electric machine tool, and has a first joint portion supporting a joint jaw, and the first joint portion is relative to a drive shaft. The second joint part is coupled to be non-rotatable (so as to rotate together) and further supports the joint jaw, and the second joint part rotates relative to the driven shaft. It relates to a type in which the coupling jaws of the second coupling part are located with some play of rotation between the coupling jaws of the first coupling part.
[0002]
Such a shaft coupling is applied to a hand-held electric machine tool such as a screwdriver or a drill.
[0003]
[Prior art]
In a known electric screwdriver having such a shaft coupling (US Pat. No. 5,016,501), a tool holder for a screw tool is coupled to a driven shaft so as not to rotate relative to the driven shaft, and the driving shaft is reversible. It is driven by an electric motor. By doing so, the screw tool can be driven clockwise and counterclockwise. In other words, the screw can be tightened or loosened.
[0004]
By providing an outer retaining ring that is in communication with the driven shaft through a rolling element with the joint portion that is coupled to the driven shaft, the joint portion that is coupled to the driven shaft can be secured to the screwdriver housing. The screwdriver can be used as a manual screwdriver.
[0005]
As a result of the play for rotation between the joint jaws of both joint parts in the shaft joint, a large noise is formed by the joint parts coming into contact with each other when the load is changed. Furthermore, vibration is generated during no-load operation, and accordingly, disturbing noise is similarly generated.
[0006]
[Problems to be solved by the invention]
The object of the present invention is to eliminate the drawbacks of the prior art.
[0007]
[Means for Solving the Problems]
In the configuration of the present invention to solve the above problems, between the first joint portion and a second joint portion, which damping device is arranged to brake the relative rotation of the two joint parts to each other, attenuation The device has a friction member that produces a frictional moment during relative rotation of both joint parts, the friction member being formed by at least one spring wire inserted on the coaxial surface of both joint parts. .
[0008]
【The invention's effect】
The shaft coupling according to the present invention having the above-described features has an advantage that the replacement cycle of the joint portion is braked and performed by the damping device that acts when the joint portion is relatively rotated.
[0009]
In this case, the damping device can be designed such that the damping moment is constant or directly proportional to the angular velocity difference between both joint portions. By doing so, firstly, when the load change is small, that is, when the torque difference between both joint parts is small, the displacement of the stop surface of the joint jaws that contact each other is prevented, and second, the torque difference is compared. If it is large, the impact is attenuated by energy conversion.
[0010]
By doing so, the inconvenient driving noise which has been generated conventionally is suppressed, and the hand-held electric machine tool equipped with the joint of the present invention has little noise, no vibration, and no so-called inertia effect due to the alternating cycle. Therefore, a feeling of quality is remarkably enhanced. The joint portion is only loaded by a small number of collisions and impacts that occur, and since these collisions and impacts are also attenuated and weakened, the durability of the joint is increased.
[0011]
By means of the measures described in claim 2 and below, advantageous configurations and improvements of the shaft coupling according to the invention are possible.
[0012]
In accordance with a preferred embodiment of the present invention, the damping device has a friction member that produces a frictional moment when the joint parts are pivoted relative to each other. This friction member is formed by at least one spring wire inserted between the coaxial surfaces of both joint portions. At least two spring wires are provided, each forming a leg of a U-shaped spring clip, with both legs in an axial slit or axial groove formed in the coaxial surface of one joint part. It is inserted so as not to move in the rotational direction, and is in contact with the coaxial surface of the other joint part.
[0013]
In this case, the biaxial slits for holding the legs of the spring clip may be arranged on the coaxial surface in the diameter direction or the secant direction. By forming with such a structure, the manufacturing cost of the damping device is extremely small. Material costs are limited to the U-shaped spring clip and the retaining groove of one joint where the spring clip is easily inserted. Because the material cost is reduced, the assembly cost is small.
[0014]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below in detail with reference to the drawings.
[0015]
The shaft coupling for a hand-held electric machine tool, in particular an electric drilling machine or an electric screwdriver, shown in FIGS. 1 and 2, comprises a first coupling part 11 and a second coupling part which are engaged with each other by a coupling jaw. 12. The first joint portion 11 is coupled to a drive shaft (not shown) of the reversible electric motor so as not to be relatively rotatable (so as to rotate together), but the second joint portion 12 is a screwdriver or a drilling machine. Is coupled to a driven shaft 13 which is coupled to a tool holding portion for fixing the tool.
[0016]
The first joint portion 11 supports two pairs of joint jaws that protrude in the axial direction from the base body 113. In this case, the joint jaws 111 of one jaw pair are formed identically and face each other at the joint part 11, and the joint jaws 112 of the second jaw pair are similarly formed identically, and the joint part 11 Although they face each other, they are offset by a circumferential angle of about 75 degrees with respect to the joint jaw 111 of the first jaw pair.
[0017]
The second joint portion 12 supports two joint jaws 121 protruding in the radial direction from the base body 122. These joint jaws 121 are arranged in such a way that in the assembled joint, one joint jaw 121 is located between the joint jaws 111 and 112 of the first joint part 11 with rotational play. Two joint portions 12 are arranged.
[0018]
Each joint jaw 111 has a radial entraining surface 111a. This entraining surface 111a cooperates with the radial stop surface 121a formed on the joint jaw 121 to rotate the second joint portion 12 in the direction opposite to the timepiece in FIG. Similarly, each joint jaw 112 has a radial entraining surface 112a. The entraining surface 112a cooperates with the radial stop surface 121b formed on the joint jaw 121 to rotate the second joint portion 12 in the clockwise direction.
[0019]
The joint jaws 111 and 112 are slipping play on the coaxial base surface 122c extending between the joint jaws 121 of the base 122 of the second joint portion 12 at the inner coaxial arcuate jaw surface 111c or 112c. Have and abut.
[0020]
When the first joint portion 11 is driven in the counterclockwise direction in FIG. 1 via the drive shaft, the joint jaws 111 abut against the stop surface 121a of the joint jaw 121 at their entraining surfaces 111a, and the joint portion 12 Is taken in the direction of rotation. On the other hand, when the joint portion 11 rotates in the clockwise direction in FIG. 1, the joint jaw 112 abuts against the stop surface 121b of the joint jaw 121 at the radial entraining surface 112a, and the second joint portion 12 is rotated during rotation. Take me with you.
[0021]
In order to reduce the noise generated when the entraining surface 111a or 112a hits the stop surfaces 121a and 121b when the load is changed, a damping device 14 that brakes the relative rotation of both joint portions is provided between the joint portions. ing. In the embodiment of FIGS. 1 and 2, the damping device 14 has a friction member that produces a frictional moment when the joint portions 11, 12 are rotated relative to each other.
[0022]
The friction member is here formed by two spring wires, which form the legs 151 and 152 of the U-shaped spring clip 15 (FIG. 2). Both leg portions 151 and 152 of the clip are located in axial slits or axial grooves 16 and 17 provided on the coaxial surface 122 c of the base body 122 of the second joint portion 12. In this case, both the leg portions 151 and 152 are held in the axial grooves 16 and 17 so as not to move in the rotational direction, and are in contact with the coaxial surface 111 c of the both joint jaws 111 of the first joint portion 11. Yes.
[0023]
However, the number of spring wires inserted on the coaxial surface 122c of the base and the coaxial surface of the joint jaw 111c can be increased, or can be at least one. The spring wire or both clip legs 151 and 152 generate a frictional moment between the joint portions 11 and 12 when the load is changed. This friction moment prevents the displacement of both joint parts 11 and 12 when the torque difference between the joint parts 11 and 12 is small, and secondly, between the joint parts 11 and 12. When the torque difference between them is relatively large, the impact when the joint jaws 11 and 12 hit each other is significantly attenuated by energy conversion from rotational energy to heat.
[0024]
For tool change, the second joint part 12 coupled to the driven shaft 13 can be fixed to the machine housing of a hand-held electric machine tool. For this purpose, a retaining ring 18 is provided that is rotatably arranged in the machine housing. The retaining ring 18 is arranged coaxially with respect to both joint parts 11, 12 and surrounds the joint jaws 111, 112 that engage each other.
[0025]
A clamping body 19 is arranged between the retaining ring 18 and the second joint part 12. These fastening bodies 19 fasten the holding ring 18 together with the second joint portion 12 when the holding ring 18 rotates. In the embodiment shown in FIGS. 1 and 2, the clamping body 19 is formed as a rolling element 20, for example a cylinder, a ball or a roller.
[0026]
These rolling elements are supported on the one hand by the inner ring surface 181 of the retaining ring 18 and on the other hand by the tangential surface section 122d of the base 122 of the second joint part 12 at the approximate center of the surface section 122d. ing. In this case, one rolling element 20 is inserted between the joint jaws 111 and 112 of the first joint part 11 with a play for rotation.
[0027]
The tangential surface section 122 d is formed by providing a beveled surface or a flattened surface on the coaxial surface 122 c of the base body 122 of the second joint portion 12, and is located at the center between the joint jaws 121. Yes.
[0028]
The distance between each rolling element 20 and the radial entraining surfaces 11b and 112b of the joint jaws 111 and 112 in the first joint portion 11 directed to the rolling element 20 is set as follows. That is, when one joint jaw 111 or 112 of the first joint part 11 abuts on the joint jaw 121 of the second joint part 12 and rotates in one or the other rotational direction, the other of the first joint parts 11 The radial entraining surface 112b or 111b of the joint jaw 112 or 111 abuts against the rolling element 20 and rotationally entrains it.
[0029]
When the first joint part 11 rotates in the direction opposite to the clockwise direction in FIG. 1, the two rolling elements 20 are entrained in the rotational direction by the radial entraining surfaces 112b of the joint jaws 112, and at this time, the tangential surface section 122d Maintain their relative position inside. When the first joint portion 11 rotates in the clockwise direction, both rolling elements 20 are entrained in the rotational direction by the radial entraining surface 111b of the both joint jaws 111, and the center position inside the tangential surface section 122d is similarly set. maintain. As a result, the rolling element 20 rolls along the tangential surface section 122 d and the inner ring surface 181 of the retaining ring 18.
[0030]
On the other hand, when the holding ring 18 is rotated relative to the joint portions 11 and 12 in one rotational direction or the other rotational direction, the rolling element 20 is displaced and the second joint portion 12 is displaced. The tangential surface section 122d of the holding ring 18 and the inner ring surface 181 of the retaining ring 18 are tightened. As a result, the second joint portion 12 is fixed to the holding ring 18 so as not to rotate, so that the second joint portion 12 coupled to the tool holding portion of the hand-held electric machine tool is fixed to the machine housing. Thereby, the tool change in the tool holding part can be performed by using, for example, an existing quick attach / detach drill chuck.
[0031]
In a hand-held electric machine tool formed as an electric screwdriver, the electric screwdriver can also be used as a manual screwdriver by securing the second joint portion 12 to the machine housing.
[0032]
The present invention is not limited to the above embodiments. For example, the damping device for braking the relative rotation between the joint parts 11 and 12 is a variable volume filled with liquid between the joint parts 11 and 12, which are in communication with each other by an overflow channel. It can also be realized by the gap. Thereby, at the time of load change, the liquid is pushed away from one gap through the overflow channel to the other gap, thereby achieving a damping action. However, the technical cost is much higher than the damping device 14 formed by the spring clip 15.
[Brief description of the drawings]
FIG. 1 is a front view of a shaft coupling of a hand-held electric machine tool according to the present invention.
2 is a development view of the shaft coupling shown in FIG. 1. FIG.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 11 Joint part, 12 Joint part, 13 Driven shaft, 14 Damping device, 15 Friction member, 16 Axial slit, 17 Axial groove, 18 Retaining ring, 19 Tightening body, 20 Rolling body, 111 Joint jaw, 111b Entraining surface 112 joint jaw, 112b entraining surface, 111c coaxial surface, 121 joint jaw, 122 base body, 122c coaxial surface, 122d surface section, 151 leg, 152 leg, 181 inner ring surface

Claims (8)

原動機のための軸継手であって、継手ジョー（１１１、１１２）を支持している第１の継手部分（１１）を有していて、この第１の継手部分（１１）が駆動軸と相対回動不能に結合されており、さらに継手ジョー（１２１）を支持している第２の継手部分（１２）を有していて、この第２の継手部分（１２）が被駆動軸（１３）と相対回動不能に結合され、第２の継手部分（１２）の継手ジョー（１２１）が第１の継手部分（１１）の継手ジョー（１１１、１１２）の間に回転用の遊びを伴って位置している形式のものにおいて、
第１の継手部分（１１）と第２の継手部分（１２）との間に、両継手部分（１１、１２）の相対回動を互いに制動する減衰装置（１４）が配置されており、
前記減衰装置（１４）が、両継手部分（１１、１２）の相対回動時に摩擦モーメントを生み出す摩擦部材（１５）を有しており、
前記摩擦部材（１５）が、両継手部分（１１、１２）の共軸面（１１１ｃ、１２２ｃ）上に挿入されている少なくとも１つのスプリングワイヤによって形成されていることを特徴とする、軸継手。A shaft coupling for the prime mover, have a first joint portion that supports the fitting jaws (111, 112) (11), the first joint part (11) and the drive shaft relative are non-rotatably engaged sintering, further have a second joint portions supporting the joint jaws (121) (12), the second joint part (12) is the driven shaft ( 13) and rotationally fixed engaged sintering, play for rotation between the joint jaw joint jaw of the second joint part (12) (121) is a first joint part (11) (111, 112) In the form located with
Between the first joint part (11) and the second joint part (12), an attenuation device (14) for braking the relative rotation of the joint parts (11, 12) is disposed .
The damping device (14) has a friction member (15) that generates a friction moment when the joint portions (11, 12) rotate relative to each other.
A shaft coupling, characterized in that the friction member (15) is formed by at least one spring wire inserted on the coaxial surfaces (111c, 122c) of both coupling parts (11, 12) . ２つのスプリングワイヤが設けられていて、両スプリングワイヤがＵ字形スプリングクリップ（１５）の脚部（１５１、１５２）を形成しており、両脚部（１５１、１５２）が、一方の継手部分（１２）の共軸面（１２２ｃ）に形成された軸方向スリットまたは軸方向溝（１６、１７）内に回転方向で移動しないように挿入されていて、他方の継手部分（１１）の共軸面（１１１ｃ）に当接している、請求項１記載の軸継手。Two spring wires are provided, and both spring wires form legs (151, 152) of a U-shaped spring clip (15), and both legs (151, 152) are connected to one joint portion (12 ) In the axial slit or axial groove (16, 17) formed in the coaxial surface (122c) of the other joint portion (11) so as not to move in the rotational direction. 111c) to abut, claim 1 shaft coupling according. 一方の継手部分（１２）の共軸面（１２２ｃ）が継手ジョー（１２１）を支持している基体（１２２）の外側リング面によって形成され、他方の継手部分（１１）の共軸面（１１１ｃ）がこの継手部分（１１）の継手ジョー（１１１）の内側の円弧状のジョー面によって形成されている、請求項１または２記載の軸継手。The coaxial surface (122c) of one joint part (12) is formed by the outer ring surface of the base (122) supporting the joint jaw (121), and the coaxial surface (111c) of the other joint part (11). The shaft joint according to claim 1 or 2 , wherein the joint portion (11) is formed by an arcuate jaw surface inside the joint jaw (111). 第２の継手部分（１２）が人手で操作可能な保持リング（１８）に固持可能である、請求項１から３までのいずれか１項記載の軸継手。The shaft coupling according to any one of claims 1 to 3 , wherein the second coupling part (12) can be fixed to a retaining ring (18) which can be operated manually. 保持リング（１８）が両継手部分（１１、１２）に対して共軸に、互いに係合する継手ジョー（１１１、１１２、１２１）を取り囲むように配置されており、保持リング（１８）と第２の継手部分（１２）との間に締付け体（１９）が配置されており、これらの締付け体（１９）が保持リング（１８）の回動時に第２の継手部分（１２）と共に当該保持リング（１８）を締め付ける、請求項４記載の軸継手。A retaining ring (18) is arranged coaxially with respect to both joint parts (11, 12) so as to surround the joint jaws (111, 112, 121) engaging with each other, The fastening body (19) is arranged between the two joint parts (12), and these fastening bodies (19) are held together with the second joint part (12) when the holding ring (18) is rotated. A shaft coupling according to claim 4 , wherein the ring (18) is tightened. 前記締付け体（１９）が転動体（２０）として形成されており、これらの転動体が一方では保持リング（１８）の内側リング面（１８１）においてかつ他方では第２の継手部分（１２）における接線方向の面区分（１２２ｄ）において該面区分のほぼ中央で転動し、それぞれ第１の継手部分（１１）の２つの継手ジョー（１１１、１１２）の間に配置されている、請求項５記載の軸継手。The clamping bodies (19) are formed as rolling elements (20), which are on the one hand on the inner ring surface (181) of the retaining ring (18) and on the other hand on the second joint part (12). in the tangential direction of the surface segment (122d) to roll approximately at the center of said surface segment is located between the two joint jaws of the first joint part respectively (11) (111, 112), according to claim 5 The shaft coupling described. 各々の転動体（２０）と当該転動体（２０）に向けられた第１の継手部分（１１）の継手ジョー（１１１、１１２）における半径方向連行面（１１１ｂ、１１２ｂ）との間隔は、第１の継手部分（１１）の一方の継手ジョー（１１１、１１２）が第２の継手部分（１２）の継手ジョー（１２１）に当接して回転連行すると、第１の継手部分（１１）の他方の継手ジョー（１１２、１１１）の半径方向連行面（１１２ｂ、１１１ｂ）が転動体（２０）に当接して回転連行するように寸法設定されている、請求項６項記載の軸継手。The distance between each rolling element (20) and the radial entraining surface (111b, 112b) in the joint jaw (111, 112) of the first joint portion (11) directed to the rolling element (20) is When one joint jaw (111, 112) of one joint part (11) comes into contact with the joint jaw (121) of the second joint part (12) and rotationally entrains, the other of the first joint part (11) The shaft coupling according to claim 6 , wherein the radial coupling surfaces (112 b, 111 b) of the coupling jaws (112, 111) are dimensioned so as to abut against the rolling elements (20) and rotationally engage. 前記減衰装置が、越流路によって互いに連通している、両継手部分の間の液体が充填された容積可変の隙間によって実現されている、請求項１記載の軸継手。  The shaft coupling according to claim 1, wherein the damping device is realized by a variable volume gap filled with liquid between the joint portions, which are in communication with each other by an overflow channel.
JP19750798A 1997-07-15 1998-07-13 Shaft coupling Expired - Fee Related JP4154035B2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1997130198 DE19730198B4 (en) 1997-07-15 1997-07-15 shaft coupling
DE19730198.3 1997-07-15

Publications (2)

Publication Number Publication Date
JPH1172122A JPH1172122A (en) 1999-03-16
JP4154035B2 true JP4154035B2 (en) 2008-09-24

Family

ID=7835702

Family Applications (1)

Application Number Title Priority Date Filing Date
JP19750798A Expired - Fee Related JP4154035B2 (en) 1997-07-15 1998-07-13 Shaft coupling

Country Status (5)

Country Link
JP (1) JP4154035B2 (en)
CN (1) CN1122140C (en)
DE (1) DE19730198B4 (en)
GB (1) GB2327254B (en)
IT (1) ITMI981522A1 (en)

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE20203391U1 (en) * 2002-03-02 2003-07-17 Trumpf Gruesch Ag Gruesch Hand-held milling machine has elastic shock absorbing assembly
DE10331662B4 (en) * 2003-07-12 2006-06-14 A & M Electric Tools Gmbh Coupling for a spindle of a machine tool
JP4854063B2 (en) * 2005-03-18 2012-01-11 株式会社マキタ Work tools
JP4746958B2 (en) * 2005-10-25 2011-08-10 株式会社マキタ Work tools
WO2006101014A1 (en) * 2005-03-18 2006-09-28 Makita Corporation Working tool
DE102005047602A1 (en) 2005-10-05 2007-04-12 Robert Bosch Gmbh Hand tool
JP4739909B2 (en) * 2005-10-25 2011-08-03 株式会社マキタ Work tools
DE102006001985A1 (en) * 2006-01-16 2007-07-19 Robert Bosch Gmbh Transmission for hand-held power tools has locating device including at least one spring damping element between carrier element and counter-element
EP2078872B1 (en) * 2008-01-08 2019-03-13 Grundfos Management A/S Bearing arrangement
DE102010011123A1 (en) * 2010-03-11 2011-09-15 Claas Selbstfahrende Erntemaschinen Gmbh Cutting unit for a harvester
DE102011005553A1 (en) * 2010-10-15 2012-04-19 Robert Bosch Gmbh Hand-held power tool with a Spindellockvorrichtung
DE102011005812A1 (en) * 2011-03-18 2012-09-20 Robert Bosch Gmbh Machine tool braking device
CN103659718B (en) * 2012-09-25 2015-08-26 上海电装燃油喷射有限公司 The shaft coupling assembling error-preventing method of fuel injection pump
CN104653646B (en) * 2015-02-13 2017-07-07 长城汽车股份有限公司 Power transmission shaft and apply its automobile
DE102015108322A1 (en) * 2015-05-27 2016-12-01 Centa-Antriebe Kirschey Gmbh Elastic jaw clutch
CN105134809B (en) * 2015-09-28 2017-12-22 安徽江淮汽车集团股份有限公司 Flexible coupling and automotive steering structure
CN105333853B (en) * 2015-11-23 2018-08-07 中国航天空气动力技术研究院 Rudder deflection angle testing device
CN113153932B (en) * 2021-04-13 2022-06-24 沈阳工业大学 Hydraulic damping flexible coupling

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE429536C (en) * 1923-04-12 1926-05-29 Rolls Royce Friction-acting damping device for clutches with resilient intermediate members, especially for motor vehicles
US1734043A (en) * 1928-02-09 1929-11-05 Carl E Nelson Hydraulic flexible coupling
GB423278A (en) * 1934-02-03 1935-01-29 Ernst Kreissig Improvements in or relating to shaft couplings
DE678363C (en) * 1936-07-17 1939-07-14 Siemens Schuckertwerke Akt Ges Coupling with energy storage devices in diesel-electric vehicles between the diesel engine and the electric generator, which serves as the drive motor when the diesel engine is started
GB833768A (en) * 1956-10-25 1960-04-27 Rolls Royce Improvements in or relating to resilient torque transmitting coupling arrangements
GB1282591A (en) * 1969-01-24 1972-07-19 Powder Couplings Ltd Improvements in or relating to drive couplings
GB1512207A (en) * 1975-07-08 1978-05-24 Imi Santon Ltd Electric switchgear
DE2825326A1 (en) * 1978-06-09 1979-12-20 Daimler Benz Ag TORQUE TRANSFER DEVICE
JPS5942502Y2 (en) * 1978-12-11 1984-12-12 日産自動車株式会社 universal joint
DE7901381U1 (en) * 1979-01-19 1979-06-13 Feighofen, Hanns Detlev, 4600 Dortmund TORQUE LIMITING FLEXIBLE SHAFT COUPLING
DE2930244C2 (en) * 1979-07-26 1983-01-13 Boge Gmbh, 5208 Eitorf Torsionally flexible coupling
DE3215765A1 (en) * 1982-04-28 1983-05-19 Daimler-Benz Ag, 7000 Stuttgart Torsional vibration damper for shafts, in particular drive shafts for internal combustion engines
US4772245A (en) * 1987-07-09 1988-09-20 Sundstrand Corportion Torque transmitting elastomeric shaft coupling with spline backup
US5016501B1 (en) * 1988-07-29 1997-07-15 Sb Power Tool Co Automatic shaft lock

Also Published As

Publication number Publication date
DE19730198A1 (en) 1999-01-21
DE19730198B4 (en) 2004-04-15
ITMI981522A1 (en) 2000-01-02
JPH1172122A (en) 1999-03-16
CN1122140C (en) 2003-09-24
GB9814288D0 (en) 1998-09-02
CN1205405A (en) 1999-01-20
GB2327254B (en) 1999-08-04
GB2327254A (en) 1999-01-20

Similar Documents

Publication Publication Date Title
JP4154035B2 (en) Shaft coupling
US5711379A (en) Hammer drill
US6306024B1 (en) Orbital tool
US3533479A (en) Impact mechanism with improved hammer and hammer frame assembly therefor
CN101980828A (en) Protective system for machine tools
JPH0289838A (en) Autotensioner for belt
JPS6044530B2 (en) Anti-vibration buffer handle for vibration equipment
US6705410B2 (en) Electrical hand-held power tool with a safety clutch
JPH10217092A (en) Hand holding type belt sander
US5850770A (en) Securing device for workpiece spindle of lathe
US6062960A (en) Orbital tool
US5435398A (en) Electrical wrench
EP1340928A4 (en) Balancer
US7635032B2 (en) Hand-held tool comprising a shaft and a lifting bearing which is mounted on the shaft
GB2430902A (en) Hand-held power tool
JP2003240663A (en) Device and method for measuring unbalanced amount of motorcycle wheel
JP4125052B2 (en) Electric screwdriver
KR960007702Y1 (en) Power testing apparatus
US5076743A (en) Device for drilling undercuts
CN106573388B (en) Oscillation drive device
JP2003028254A (en) Electric wheel driving device
JPS5815135A (en) Torque meter for grinder
JP2002264031A (en) Power tool
JP3641236B2 (en) Brake device
JP2001191255A (en) Rotary hammering tool

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20050712

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20070926

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20071004

A601 Written request for extension of time

Free format text: JAPANESE INTERMEDIATE CODE: A601

Effective date: 20080104

A602 Written permission of extension of time

Free format text: JAPANESE INTERMEDIATE CODE: A602

Effective date: 20080109

A601 Written request for extension of time

Free format text: JAPANESE INTERMEDIATE CODE: A601

Effective date: 20080130

A602 Written permission of extension of time

Free format text: JAPANESE INTERMEDIATE CODE: A602

Effective date: 20080204

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20080226

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20080605

A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20080707

R150 Certificate of patent or registration of utility model

Free format text: JAPANESE INTERMEDIATE CODE: R150

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20110711

Year of fee payment: 3

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20120711

Year of fee payment: 4

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130711

Year of fee payment: 5

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

LAPS Cancellation because of no payment of annual fees