JPH0461214B2 - - Google Patents
Info
- Publication number
- JPH0461214B2 JPH0461214B2 JP61266589A JP26658986A JPH0461214B2 JP H0461214 B2 JPH0461214 B2 JP H0461214B2 JP 61266589 A JP61266589 A JP 61266589A JP 26658986 A JP26658986 A JP 26658986A JP H0461214 B2 JPH0461214 B2 JP H0461214B2
- Authority
- JP
- Japan
- Prior art keywords
- armature
- sliding ring
- electromagnetic clutch
- brake
- gap
- 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
- 230000004323 axial length Effects 0.000 claims description 7
- 230000000694 effects Effects 0.000 description 6
- 230000008878 coupling Effects 0.000 description 3
- 238000010168 coupling process Methods 0.000 description 3
- 238000005859 coupling reaction Methods 0.000 description 3
- 230000005284 excitation Effects 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
Landscapes
- Braking Arrangements (AREA)
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は電磁クラツチ・ブレーキにおける自動
空隙調整装置、詳しくは板ばね駆動方式の電磁ク
ラツチ・ブレーキのアーマチユア釈放時、アーマ
チユアとロータ・フイールドの摩擦板との空隙を
常に一定に調整するための自動空隙調整装置に関
するものである。Detailed Description of the Invention (Industrial Application Field) The present invention relates to an automatic air gap adjustment device for an electromagnetic clutch/brake, and more specifically, when the armature of a leaf spring driven electromagnetic clutch/brake is released, the friction between the armature and the rotor field is reduced. This invention relates to an automatic gap adjustment device for always adjusting the gap between the plate and the plate.
（従来の技術）
電磁クラツチ・ブレーキのアーマチユア釈放時
にはアーマチユアとロータ・フイールドの摩擦板
との空隙は常に一定値（たとえば0.5mm）に保持
し、コイル励磁によるアーマチユア吸引時間を常
に一定にしておく必要がある。これは電磁クラツ
チ・ブレーキの連結・制動回路の増加によつて摩
擦面が摩耗して空隙が広くなると、コイル励磁に
よるアーマチユア吸引時間が長くなつて連結・制
動の作動が遅くなり、さらに空隙が広くなつた場
合は、コイルを励磁してもアーマチユアに吸引力
が及ばず、連結・制動の作動をしなくなるという
欠陥を生ずるため、これを防止する必要があるか
らである。(Prior art) When the armature of an electromagnetic clutch/brake is released, the gap between the armature and the friction plate of the rotor field must always be maintained at a constant value (for example, 0.5 mm), and the armature suction time due to coil excitation must be kept constant. There is. This is because as the number of coupling and braking circuits for electromagnetic clutches and brakes increases, the friction surfaces wear out and the gap widens, and the armature suction time due to coil excitation becomes longer, slowing down the coupling and braking operations, and the gap widens. This is because if the coil is energized, the attraction force will not be applied to the armature and the coupling and braking will not work, resulting in a problem that it is necessary to prevent this.
第４図〜第６図に示されるのは本発明者による
実願昭61−8413号（実開昭62−194218号）の明細
書に記載された電磁クラツチ・ブレーキにおける
自動空隙調整装置の一実施例である。 Figures 4 to 6 show an example of an automatic air gap adjustment device for an electromagnetic clutch/brake described in the specification of Utility Application No. 1984-8413 (Utility Model Application No. 1942-1988) by the present inventor. This is an example.
第４図および第５図に示される電磁クラツチ・
ブレーキは実公昭58−13143号公報に記載のもの
と自動空隙調整装置部分以外は実質的に同一構成
のものであるので、主として自動空隙調整装置部
分について述べる。アーマチユア１が複数個（第
４図のものは第５図に示されるように３個）の板
ばね２を介してハブ３に固着され、ハブ３の周辺
部に設けられた数個の貫通穴に摺動リング４が所
定の把持力をもつように圧入され反アーマチユア
側の後端部を所定量だけ突出させている。駆動ピ
ン５は先端にアーマチユア１と板ばね２とを固着
するねじ部を有するとともに後端に摺動リング４
の内径より大きな外径を有するフランジ部を有
し、その中間軸部が摺動リング４に摺動自在に挿
通されている。摺動リング４と駆動ピン５のフラ
ンジ部との軸方向空隙G1は、第６図Ａに示され
るようにに、アーマチユア釈放時のアーマチユア
１とロータ・フイールドの摩擦板６との軸方向空
隙G2に等しくＬに設定されている。 The electromagnetic clutch shown in FIGS. 4 and 5
Since the brake has substantially the same construction as that described in Japanese Utility Model Publication No. 13143/1983, except for the automatic gap adjustment device, the automatic gap adjustment device will be mainly described. The armature 1 is fixed to the hub 3 via a plurality of leaf springs 2 (the one in FIG. 4 is three as shown in FIG. 5), and several through holes are provided around the hub 3. A sliding ring 4 is press-fitted with a predetermined gripping force, and the rear end portion on the side opposite to the armature protrudes by a predetermined amount. The drive pin 5 has a threaded portion at its tip for fixing the armature 1 and the leaf spring 2, and a sliding ring 4 at its rear end.
It has a flange portion having an outer diameter larger than the inner diameter of the flange portion, and an intermediate shaft portion of the flange portion is slidably inserted into the sliding ring 4. The axial gap G1 between the sliding ring 4 and the flange portion of the drive pin 5 is equal to the axial gap between the armature 1 and the friction plate 6 of the rotor field when the armature is released, as shown in FIG. 6A. G is set to L equal to 2 .
そのような構造の自動空隙調整装置の作用は次
のとおりである。使用初期におけるアーマチユア
吸着時には、第６図Ｂに示されるように、アーマ
チユア１は摩擦板６に吸着して空隙G2は０とな
るとともに駆動ピン５のフランジ部も右方へ移動
して摺動リング４と接して空隙G1も０となる。
摩擦面が摩耗した場合には、第６図Ｃに示される
ようにアーマチユア１がコイル励磁によりロー
タ・フイールドの摩擦板６に向かつて右方へ吸引
されるときに駆動ピン５のフランジ部も右方へ移
動しフランジ部が摺動リング４の反アーマチユア
側面に当たつてアーマチユア１は摩擦板６に吸着
しないが、吸引力は板ばね２の弾力およびハブ３
の摺動リング４を把持する力に打ち勝つてアーマ
チユア１を右方へ吸引するので、摺動リング４は
摩擦面の摩耗量だけ右方へ摺動してアーマチユア
１は摩擦板６に吸着し、アーマチユア釈放時、駆
動ピン５のフランジ部と摺動リング４の反アーマ
チユア側面との空隙は前記一定値Ｌに保たれる。
即ち、摺動リング４がハブ３の貫通穴内面を摩擦
面の摩耗量だけアーマチユア方向に摺動すること
によつて摩擦面の空隙は常に一定に保たれるので
ある。 The operation of the automatic air gap adjusting device having such a structure is as follows. When the armature is attracted at the initial stage of use, as shown in FIG. 6B, the armature 1 is attracted to the friction plate 6 and the gap G2 becomes 0, and the flange of the drive pin 5 also moves to the right and slides. In contact with the ring 4, the air gap G1 also becomes 0.
If the friction surface is worn, as shown in FIG. 6C, when the armature 1 is attracted to the right by the coil excitation toward the friction plate 6 of the rotor field, the flange of the drive pin 5 also moves to the right. The armature 1 does not attract the friction plate 6 as the flange portion hits the opposite side of the armature of the sliding ring 4, but the suction force is due to the elasticity of the leaf spring 2 and the hub 3.
The force of gripping the sliding ring 4 is overcome and the armature 1 is attracted to the right, so the sliding ring 4 slides to the right by the amount of wear on the friction surface, and the armature 1 is attracted to the friction plate 6. When the armature is released, the gap between the flange portion of the drive pin 5 and the side surface of the sliding ring 4 opposite to the armature is maintained at the constant value L.
That is, the sliding ring 4 slides on the inner surface of the through hole of the hub 3 in the armature direction by the amount of wear on the friction surface, so that the gap between the friction surfaces is always kept constant.
（発明が解決しようとする問題点）
しかしながら実願昭61−8413号の明細書に記載
された電磁クラツチ・ブレーキにおける自動空隙
調整装置には次のような問題がある。(Problems to be Solved by the Invention) However, the automatic gap adjustment device for an electromagnetic clutch/brake described in the specification of Utility Model Application No. 1984-8413 has the following problems.
(1) 電磁クラツチ・ブレーキは通常吸引特性、釈
放特性にバランスのとれたもの、例えば吸引時
間＝釈放時間のものが望まれる。また吸引特性
は電源側で所望のように改善可能であるが、釈
放特性は主として板ばね２の釈放力で決定され
るため釈放特性が重要な選定基準となるケース
が多い。ところが、アーマチユア１は前述のよ
うに複数の板ばね２を介してハブ３に固着され
ており、板ばね２の断面形状は機能的に薄く幅
広のものが要求されるために、アーマチユア１
の吸引時間は短く吸引特性は良いが、アーマチ
ユア１の釈放力は弱く、従つて釈放時間が長く
釈放特性が劣る。(1) Electromagnetic clutches and brakes are normally desired to have well-balanced attraction and release characteristics, for example, one in which the attraction time equals the release time. Further, the attraction characteristics can be improved as desired on the power source side, but the release characteristics are mainly determined by the release force of the leaf spring 2, so the release characteristics are often an important selection criterion. However, as mentioned above, the armature 1 is fixed to the hub 3 via a plurality of leaf springs 2, and the cross-sectional shape of the leaf springs 2 is required to be functionally thin and wide.
The suction time is short and the suction characteristics are good, but the release force of the armature 1 is weak, so the release time is long and the release characteristics are poor.
(2) 上述の構造の電磁クラツチ・ブレーキは摩擦
面の摩耗に対して摩耗分だけ板ばね２が摩擦面
側に撓み、引続いて吸引・釈放を行なうため、
摩耗に伴つて板ばね２の釈放力が大きく変化す
る。つまり使用初期は吸引時間が短く釈放時間
は長いが、摩耗に伴つて吸引時間が長く釈放時
間が短くなり、吸引・釈放特性が大きく変化す
る。(2) In the electromagnetic clutch/brake having the above structure, as the friction surface wears, the leaf spring 2 bends toward the friction surface by the amount of wear, and subsequently attracts and releases.
The release force of the leaf spring 2 changes significantly with wear. In other words, at the beginning of use, the suction time is short and the release time is long, but as it wears down, the suction time becomes longer and the release time becomes shorter, and the suction and release characteristics change significantly.
（問題点を解決するための手段）
本発明は上述の問題点を解決し、
(1) 板ばねの釈放力（リリーズ力）を高めること
による釈放特性の改善、
(2) 前項の波及効果である摩耗追従に対する吸
引・釈放特性変化の改善、
を達成することができるように、
第一の発明として、一端をハブに固着し他端を
アーマチユアに固着した板ばねにより駆動する電
磁クラツチ・ブレーキにおいて、前記ハブの周辺
部に設けられた数度の貫通穴にそれぞれ所定の把
持力をもつように摺動リングを圧入して後端部を
所定量だけ突出させ、先端に前記アーマチユアと
前記板ばねとを固着する手段を有するとともに後
端に前記摺動リングの内径より大きな外径を有す
るフランジ部を有する駆動ピンの軸部を前記摺動
リングに摺動自在に挿通し、前記摺動リングの端
面と前記駆動ピンの前記フランジ部との軸方向空
隙内に前記軸方向に圧縮可能に弾性部材を介装し
ておき、前記アーマチユア釈放時の前記摺動リン
グの端面と前記フランジ部との軸方向空隙は前記
アーマチユアとロータ・フイールドの摩擦板との
軸方向空隙と前記弾性部材の圧縮時の前記摺動リ
ング端面からの軸方向長さとの和に等しく設定さ
れている自動空隙調整装置を提供しようとするも
のであり、
第二の発明として、前記摺動リングの反アーマ
チユア側端部分に設けられた段差部と前記駆動ピ
ンの前記フランジ部との軸方向空隙内に前記軸方
向に圧縮可能に弾性部材を介装しておき、前記ア
ーマチユア釈放時の前記摺動リングの端面と前記
フランジ部との軸方向空隙は前記アーマチユアと
ロータ・フイールドの摩擦板との軸方向空隙に等
しく設定されている自動空隙調整装置を提供しよ
うとするものである。(Means for Solving the Problems) The present invention solves the above-mentioned problems by (1) improving the release characteristics by increasing the release force of the leaf spring, and (2) achieving the ripple effect of the previous section. In order to improve the change in attraction and release characteristics with respect to a certain amount of wear, the first invention provides an electromagnetic clutch/brake driven by a leaf spring whose one end is fixed to a hub and the other end is fixed to an armature. A sliding ring is press-fitted into several through-holes provided around the hub so as to have a predetermined gripping force, so that the rear end protrudes by a predetermined amount, and the armature and the leaf spring are attached to the tip. A shaft portion of a drive pin having a flange portion having an outer diameter larger than the inner diameter of the sliding ring at the rear end is slidably inserted into the sliding ring, and the shaft portion of the driving pin is slidably inserted into the sliding ring. An elastic member compressible in the axial direction is interposed in the axial gap between the end face and the flange portion of the drive pin, and when the armature is released, the axis between the end face of the sliding ring and the flange portion is interposed. Provided is an automatic gap adjustment device in which the directional gap is set equal to the sum of the axial gap between the armature and the friction plate of the rotor field and the axial length of the elastic member from the end face of the sliding ring when compressed. As a second invention, the sliding ring is compressible in the axial direction within the axial gap between the stepped portion provided at the end portion on the opposite armature side and the flange portion of the drive pin. an elastic member is interposed in the armature, and the axial gap between the end face of the sliding ring and the flange portion when the armature is released is set equal to the axial gap between the armature and the friction plate of the rotor field. The purpose of this invention is to provide an automatic air gap adjustment device.
（実施例）
以下本発明による電磁クラツチ・ブレーキにお
ける自動空隙調整装置の実施例について第１図〜
第３図を参照して説明する。(Example) The following is an example of an automatic air gap adjusting device for an electromagnetic clutch/brake according to the present invention in Figs.
This will be explained with reference to FIG.
第１図は本発明の第一実施例であり、第１図に
示される電磁クラツチ・ブレーキは第４図〜第６
図に示される実願昭61−8413号の明細書に記載の
ものと自動空隙調整装置部分以外は実質的に同一
構成のものであるので、その異なつている部分に
ついて述べる。 FIG. 1 shows a first embodiment of the present invention, and the electromagnetic clutch/brake shown in FIG.
The structure is substantially the same as that described in the specification of Japanese Utility Model Application No. 1984-8413, except for the automatic gap adjustment device shown in the figure, so the different parts will be described below.
アーマチユア１１が複数個（本第一実施例のも
のは第５図と同様に３個）の板ばね１２を介して
ハブ１３に固着され、ハブ１３の周辺部に設けら
れた数個の貫通穴に摺動リング１４が所定の把持
力をもつように圧入され、反アーマチユア側の後
端部を所定量だけ突出させている。駆動ピン１５
は先端にアーマチユア１１と板ばね１２とを固着
するねじ部を有するとともに後端に摺動リング１
４の内径より大きな外径を有するフランジ部を有
し、その中間軸部が摺動リング１４に摺動自在に
挿通されている。 The armature 11 is fixed to the hub 13 via a plurality of leaf springs 12 (three in the first embodiment as in FIG. 5), and several through holes provided around the hub 13. A sliding ring 14 is press-fitted into the armature so as to have a predetermined gripping force, and the rear end portion on the side opposite to the armature protrudes by a predetermined amount. Drive pin 15
has a threaded portion at the tip for fixing the armature 11 and the leaf spring 12, and a sliding ring 1 at the rear end.
It has a flange portion having an outer diameter larger than the inner diameter of the ring 4, and its intermediate shaft portion is slidably inserted into the sliding ring 14.
１６は弾性部材、本第一実施例においては皿ば
ねまたは波ばねであり、摺動リング１４の反アー
マチユア側の端面と駆動ピン１５のフランジ部と
の軸方向空隙内に前記軸方向に圧縮可能に介装さ
れている。そしてアーマチユア釈放時の摺動リン
グ１４の端面と駆動ピン１５のフランジ部との軸
方向空隙G3は、第１図Ａに示されるように、ア
ーマチユア１１とロータ・フイールドの摩擦板１
７との軸方向空隙G4＝Ｌと皿ばね等の弾性部材
１６の圧縮時の摺動リング１４の端面からの軸方
向長さｌとの和に等しく設定されている。 Reference numeral 16 denotes an elastic member, which is a disc spring or a wave spring in the first embodiment, and is compressible in the axial direction within the axial gap between the end surface of the sliding ring 14 on the side opposite to the armature and the flange portion of the drive pin 15. is interposed in. When the armature is released, the axial gap G3 between the end face of the sliding ring 14 and the flange portion of the drive pin 15 is the gap G3 between the armature 11 and the friction plate 1 of the rotor field, as shown in FIG. 1A.
7 is set equal to the sum of the axial gap G 4 =L and the axial length l from the end surface of the sliding ring 14 when the elastic member 16, such as a disc spring, is compressed.
また皿ばね等の弾性部材の撓み荷重は、アーマ
チユア吸引力＞摺動リングのハブ圧入保持力＞板
ばね撓み荷重＋弾性部材の撓み荷重が満足される
ように設定される。 Further, the deflection load of the elastic member such as a disc spring is set so that the following relationship is satisfied: armature suction force>hub press-fit holding force of sliding ring>plate spring deflection load+elastic member deflection load.
そのような構造の自動空隙調整装置の作用は次
のとおりである。使用初期におけるアーマチユア
吸着時には、第１図Ｂに示されるように、アーマ
チユア１１は摩擦板１７に吸着して空隙G4は０
となるとともに駆動ピン１５のフランジ部も右方
へ移動して摺動リング１４に対して皿ばね等の弾
性部材１６を押圧して空隙G3はｌとなる。 The operation of the automatic air gap adjusting device having such a structure is as follows. When the armature is adsorbed in the initial stage of use, the armature 11 is adsorbed to the friction plate 17, and the gap G4 becomes zero, as shown in FIG. 1B.
At the same time, the flange portion of the drive pin 15 also moves to the right, pressing the elastic member 16 such as a disc spring against the sliding ring 14, and the gap G3 becomes l.
摩擦面が摩耗した場合の作用については第６図
Ｃを参照して説明したのと同様であり、摺動リン
グ１４がハブ１３の貫通穴内面を摩擦面の摩耗量
だけアーマチユア方向に摺動することによつて摩
擦面の空隙は常に一定に保たれるのである。 The effect when the friction surface is worn is the same as that described with reference to FIG. 6C, and the sliding ring 14 slides on the inner surface of the through hole of the hub 13 in the armature direction by the amount of wear on the friction surface. As a result, the gap between the friction surfaces is always kept constant.
第２図は本発明の第二実施例であり、第１図に
示される電磁クラツチ・ブレーキと異なつた部分
を示しているのでその異なつた部分について述べ
る。 FIG. 2 shows a second embodiment of the present invention, and shows parts different from the electromagnetic clutch/brake shown in FIG. 1, so the different parts will be described below.
１８は弾性部材、本第二実施例においてはコイ
ルスプリングまたはゴム部材であり、皿ばねまた
は波ばねでもよく、摺動リング１９反アーマチユ
ア側端部分に設けられた段差部と駆動ピン２０の
フランジ部との軸方向空隙内に介装されており、
しかもその摺動リングの段差部からの摺動リング
の端面までの軸方向長さは弾性部材１８の圧縮時
の軸方向長さより大きく設定されている。そして
アーマチユア釈放時の摺動リング１９の端面と駆
動ピン２０のフランジ部との軸方向空隙G5は、
第２図Ａに示されるように、アーマチユア１１と
ロータ・フイールドの摩擦板１７との軸方向空隙
G6＝Ｌに等しく設定されている。 Reference numeral 18 denotes an elastic member, which in the second embodiment is a coil spring or a rubber member, and may be a disc spring or a wave spring. It is inserted in the axial gap between the
Moreover, the axial length from the stepped portion of the sliding ring to the end face of the sliding ring is set to be larger than the axial length of the elastic member 18 when compressed. The axial gap G5 between the end face of the sliding ring 19 and the flange portion of the drive pin 20 when the armature is released is:
As shown in FIG. 2A, there is an axial gap between the armature 11 and the rotor field friction plate 17.
G 6 is set equal to L.
使用初期におけるアーマチユア吸着時には、第
２図Ｂに示されるように、アーマチユア１１は摩
擦板１７に吸着して空隙G6は０となるとともに、
駆動ピン２０のフランジ部も右方に摺動して空隙
G5は０となる。摩擦面が摩耗した場合の作用に
ついては第６図Ｃを参照して説明したのと同様で
ある。 When the armature is adsorbed in the initial stage of use, as shown in FIG. 2B, the armature 11 is adsorbed to the friction plate 17, and the gap G6 becomes 0.
The flange part of the drive pin 20 also slides to the right to fill the gap.
G5 becomes 0. The effect when the friction surface is worn is the same as that described with reference to FIG. 6C.
上述の第４図に示される従来の電磁クラツチ・
ブレーキに第一実施例の如き皿ばね等の弾性部材
１６または第二実施例の如きコイルスプリング等
の弾性部材１８を追加することによつて第３図に
示す如くアーマチユア釈放時の釈放力（リリーズ
力）が向上する。 The conventional electromagnetic clutch shown in FIG.
By adding an elastic member 16 such as a disc spring as in the first embodiment or an elastic member 18 such as a coil spring as in the second embodiment to the brake, the release force (release force) when the armature is released can be increased as shown in FIG. power) improves.
（発明の効果）
本発明による電磁クラツチ・ブレーキにおける
自動空隙調整装置は、上述のように構成されてい
るので、次の効果がある。(Effects of the Invention) Since the automatic air gap adjustment device for an electromagnetic clutch/brake according to the present invention is configured as described above, it has the following effects.
(1) 皿ばね、コイルスプリング等を適当に設計、
装着することによつてアーマチユア釈放力の向
上が可能となり、釈放特性の改善ができる。(1) Appropriately design disc springs, coil springs, etc.
By installing it, the armature release force can be improved and the release characteristics can be improved.
(2) (1)項の波及効果として、完全摩耗に至る迄ほ
ぼ安定した吸引・釈放特性が得られる。(2) As a ripple effect of item (1), almost stable suction and release characteristics can be obtained until complete wear is achieved.
(3) 従来技術においては、使用初期アーマチユア
釈放時のバネ与圧０であるため空転時に外部あ
るいは自己振動等によりアーマチユアが前後に
振動し異音や機械的軽い損傷を発生する場合が
あるが、本発明によりバネを圧縮装着すれば適
度な与圧も与えられ、こういつた問題も解決出
来る。(3) In the conventional technology, since the spring pressure is 0 when the armature is released at the initial stage of use, the armature may vibrate back and forth due to external or self-vibration during idling, causing abnormal noise and minor mechanical damage. If the spring is compressed and mounted according to the present invention, an appropriate pressurization can be applied, and this problem can be solved.
第１図Ａは本発明による電磁クラツチ・ブレー
キにおける自動空隙調整装置の第一実施例のアー
マチユア釈放時の断面側面図、第１図Ｂは第１図
Ａのアーマチユア吸着時の断面側面図、第２図Ａ
は本発明の第二実施例のアーマチユア釈放時の部
分断面側面図、第２図Ｂは第２図Ａのアーマチユ
ア吸着時の部分断面側面図、第３図は本発明によ
るアーマチユア釈放力の向上を示すグラフ、第４
図は従来の電磁クラツチ・ブレーキにおける自動
空隙調整装置を示す断面側面図、第５図は第４図
の右正面図、第６図は第４図の装置の作動状態図
であつて、Ａはアーマチユア釈放時、Ｂはアーマ
チユア吸着時、Ｃは摩耗追従時を示す。
１…アーマチユア、２…板ばね、３…ハブ、４
…摺動リング、５…駆動ピン、６…ロータ・フイ
ールドの摩擦板、１１…アーマチユア、１２…板
ばね、１３…ハブ、１４…摺動リング、１５…駆
動ピン、１６…弾性部材、１７…ロータ・フイー
ルドの摩擦板、１８…弾性部材、１９…摺動リン
グ、２０…駆動ピン。
FIG. 1A is a cross-sectional side view of the first embodiment of the automatic gap adjustment device for an electromagnetic clutch/brake according to the present invention when the armature is released, FIG. 1B is a cross-sectional side view of FIG. 1A when the armature is attracted, and FIG. Figure 2A
2B is a partial sectional side view of the second embodiment of the present invention when the armature is released, FIG. 2B is a partial sectional side view of the armature of FIG. 2A when it is attracted, and FIG. Graph shown, 4th
The figure is a cross-sectional side view showing an automatic air gap adjustment device in a conventional electromagnetic clutch/brake, FIG. 5 is a right front view of FIG. 4, and FIG. 6 is a diagram of the operating state of the device in FIG. When the armature is released, B indicates when the armature is attracted, and C indicates when the armature follows wear. 1... Armature, 2... Leaf spring, 3... Hub, 4
...Sliding ring, 5... Drive pin, 6... Friction plate of rotor field, 11... Armature, 12... Leaf spring, 13... Hub, 14... Sliding ring, 15... Drive pin, 16... Elastic member, 17... Friction plate of rotor field, 18... elastic member, 19... sliding ring, 20... drive pin.
Claims (1)
着した板ばねにより駆動する電磁クラツチ・ブレ
ーキにおいて、前記ハブの周辺部に設けられた数
個の貫通穴にそれぞれ所定の把持力をもつように
摺動リングを圧入して後端部を所定量だけ突出さ
せ、先端に前記アーマチユアと前記板ばねとを固
着する手段を有するとともに後端に前記摺動リン
グの内径より大きな外径を有するフランジ部を有
する駆動ピンの軸部を前記摺動リングに摺動自在
に挿通し、前記摺動リングの端面と前記駆動ピン
の前記フランジ部との軸方向空隙内に前記軸方向
に圧縮可能に弾性部材を介装しておき、前記アー
マチユア釈放時の前記摺動リングの端面と前記フ
ランジ部との軸方向空隙は前記アーマチユアとロ
ータ・フイールドの摩擦板との軸方向空隙と前記
弾性部材の圧縮時の前記摺動リング端面からの軸
方向長さとの和に等しく設定されていることを特
徴とする電磁クラツチ・ブレーキにおける自動空
隙調整装置。 ２ 特許請求の範囲第１項記載の電磁クラツチ・
ブレーキにおける自動空隙調整装置において、前
記弾性部材は皿ばねまたは波ばねである電磁クラ
ツチ・ブレーキにおける自動空隙調整装置。 ３ 一端をハブに固着し他端をアーマチユアに固
着した板ばねにより駆動する電磁クラツチ・ブレ
ーキにおいて、前記ハブの周辺部に設けられた数
個の貫通穴にそれぞれ所定の把持力をもつように
摺動リングを圧入して後端部を所定量だけ突出さ
せ、先端に前記アーマチユアと前記板ばねとを固
着する手段を有するとともに後端に前記摺動リン
グの内径より大きな外径を有するフランジ部を有
する駆動ピンの軸部を前記摺動リングに摺動自在
に挿通し、前記摺動リングの反アーマチユア側端
部分に設けられた段差部と前記駆動ピンの前記フ
ランジ部との軸方向空隙内に前記軸方向に圧縮可
能に弾性部材を介装しておき、前記アーマチユア
釈放時の前記摺動リングの端面と前記フランジ部
との軸方向空隙は前記アーマチユアとロータ・フ
イールドの摩擦板との軸方向空隙に等しく設定さ
れていることを特徴とする電磁クラツチ・ブレー
キにおける自動空隙調整装置。 ４ 特許請求の範囲第３項記載の電磁クラツチ・
ブレーキにおける自動空隙調整装置において、前
記弾性部材はコイルスプリングまたはゴム部材で
ある電磁クラツチ・ブレーキにおける自動空隙調
整装置。 ５ 特許請求の範囲第３項記載の電磁クラツチ・
ブレーキにおける自動空隙調整装置において、前
記摺動リングの段差部から摺動リングの端面まで
の軸方向長さは前記弾性部材の圧縮時の軸方向長
さより大きく設定されている電磁クラツチ・ブレ
ーキにおける自動空隙調整装置。[Scope of Claims] 1. In an electromagnetic clutch/brake driven by a leaf spring whose one end is fixed to a hub and the other end is fixed to an armature, predetermined grips are provided in several through holes provided around the hub, respectively. The sliding ring is press-fitted with force so that the rear end protrudes by a predetermined amount, and the tip has means for fixing the armature and the leaf spring, and the rear end has an outer diameter larger than the inside diameter of the sliding ring. A shaft portion of a driving pin having a flange portion having a diameter is slidably inserted into the sliding ring, and the shaft portion of the driving pin is inserted into the axial direction in the axial gap between the end face of the sliding ring and the flange portion of the driving pin. A compressible elastic member is interposed, and the axial gap between the end face of the sliding ring and the flange portion when the armature is released is equal to the axial gap between the armature and the friction plate of the rotor field and the elastic member. An automatic gap adjustment device for an electromagnetic clutch/brake, characterized in that the gap is set equal to the sum of the axial length from the end face of the sliding ring when the member is compressed. 2. The electromagnetic clutch described in claim 1.
An automatic air gap adjustment device for an electromagnetic clutch/brake, wherein the elastic member is a disc spring or a wave spring. 3. In an electromagnetic clutch/brake driven by a leaf spring fixed at one end to a hub and at the other end to an armature, the clutch is slid into several through holes provided around the hub so as to each have a predetermined gripping force. A sliding ring is press-fitted so that its rear end protrudes by a predetermined amount, and the tip thereof has means for fixing the armature and the leaf spring, and the rear end has a flange portion having an outer diameter larger than the inner diameter of the sliding ring. A shaft portion of a drive pin having a drive pin is slidably inserted into the sliding ring, and is inserted into an axial gap between a stepped portion provided at an end portion of the sliding ring on the side opposite to the armature and the flange portion of the driving pin. An elastic member is interposed so as to be compressible in the axial direction, and when the armature is released, the axial gap between the end face of the sliding ring and the flange portion is in the axial direction between the armature and the friction plate of the rotor field. An automatic air gap adjustment device for an electromagnetic clutch/brake, characterized in that the air gap is set equal to the air gap. 4. The electromagnetic clutch described in claim 3.
An automatic gap adjustment device for an electromagnetic clutch/brake, wherein the elastic member is a coil spring or a rubber member. 5. The electromagnetic clutch described in claim 3.
In the automatic air gap adjustment device for a brake, the axial length from the stepped portion of the sliding ring to the end face of the sliding ring is set to be larger than the axial length of the elastic member when compressed. Air gap adjustment device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61266589A JPS63120921A (en) | 1986-11-11 | 1986-11-11 | Automatic gap adjustment device in electromagnetic clutch/brake |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61266589A JPS63120921A (en) | 1986-11-11 | 1986-11-11 | Automatic gap adjustment device in electromagnetic clutch/brake |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63120921A JPS63120921A (en) | 1988-05-25 |
| JPH0461214B2 true JPH0461214B2 (en) | 1992-09-30 |
Family
ID=17432907
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP61266589A Granted JPS63120921A (en) | 1986-11-11 | 1986-11-11 | Automatic gap adjustment device in electromagnetic clutch/brake |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS63120921A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103429927B (en) | 2012-01-17 | 2016-03-30 | 株式会社小松制作所 | Work vehicle and braking device thereof |
| GB2505540B (en) * | 2012-01-17 | 2014-07-09 | Komatsu Mfg Co Ltd | Work vehicle and brake device thereof |
| CN103307138B (en) * | 2012-03-06 | 2016-03-02 | 张希祥 | Spin canting clutch |
| LU93045B1 (en) * | 2016-04-27 | 2017-11-07 | Ovalo Gmbh | Motorized joint for a programmable motion machine |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3762522A (en) * | 1972-05-10 | 1973-10-02 | Stearns Electric Corp | Self-adjusting clutch or brake |
| JPS562042U (en) * | 1979-06-16 | 1981-01-09 | ||
| JPS6122935B2 (en) * | 1984-01-12 | 1986-06-03 | Yoo Yakobusu Unto Co Gmbh |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6122935U (en) * | 1984-07-17 | 1986-02-10 | 小倉クラツチ株式会社 | Electromagnetic coupling device |
-
1986
- 1986-11-11 JP JP61266589A patent/JPS63120921A/en active Granted
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3762522A (en) * | 1972-05-10 | 1973-10-02 | Stearns Electric Corp | Self-adjusting clutch or brake |
| JPS562042U (en) * | 1979-06-16 | 1981-01-09 | ||
| JPS6122935B2 (en) * | 1984-01-12 | 1986-06-03 | Yoo Yakobusu Unto Co Gmbh |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS63120921A (en) | 1988-05-25 |
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