JPH0227543B2 - - Google Patents
Info
- Publication number
- JPH0227543B2 JPH0227543B2 JP58227704A JP22770483A JPH0227543B2 JP H0227543 B2 JPH0227543 B2 JP H0227543B2 JP 58227704 A JP58227704 A JP 58227704A JP 22770483 A JP22770483 A JP 22770483A JP H0227543 B2 JPH0227543 B2 JP H0227543B2
- Authority
- JP
- Japan
- Prior art keywords
- torque
- shaft
- lever
- transmitted
- support
- 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
Classifications
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05G—CONTROL DEVICES OR SYSTEMS INSOFAR AS CHARACTERISED BY MECHANICAL FEATURES ONLY
- G05G7/00—Manually-actuated control mechanisms provided with one single controlling member co-operating with one single controlled member; Details thereof
- G05G7/02—Manually-actuated control mechanisms provided with one single controlling member co-operating with one single controlled member; Details thereof characterised by special provisions for conveying or converting motion, or for acting at a distance
-
- 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
- F16H—GEARING
- F16H35/00—Gearings or mechanisms with other special functional features
- F16H35/10—Arrangements or devices for absorbing overload or preventing damage by overload
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Automation & Control Theory (AREA)
- Mechanical Control Devices (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Transmission Devices (AREA)
Description
【発明の詳細な説明】
本発明は、トルク被伝達軸以降の機器類に対し
過トルクを伝達しないようにした過トルク伝達防
止用レバー装置に関し、更に詳しくは、可変動翼
軸流フアンの動翼制御レバー、可変静翼軸流、遠
心フアンの静翼制御レバー、フアン、ブロワ、コ
ンプレツサにおけるガイドベーンの制御レバー等
に採用して威力を発揮する過トルク伝達防止用レ
バー装置に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an overtorque transmission prevention lever device that prevents overtorque from being transmitted to equipment after the torque transmitted shaft, and more specifically, the present invention relates to a lever device for preventing overtorque from being transmitted to equipment after the torque transmitted shaft. The present invention relates to a lever device for preventing overtorque transmission, which is effective when used in blade control levers, variable stator blade axial flow, stator blade control levers of centrifugal fans, control levers of guide vanes in fans, blowers, compressors, etc.
第１図乃至第３図は可変動翼軸流フアンの一般
的な構成例を示すもので、複数の可変動翼１を有
した回転ハブ２，３（図示の場合はダブル構造の
例を示している）が、主軸受部４に支持され、電
動機５により回転駆動されて導入口６からの流体
を矢印７で示すように圧縮してデイフユーザ８に
導くよう構成されている。 Figures 1 to 3 show general configuration examples of variable-blade axial flow fans. is supported by a main bearing 4 and rotationally driven by an electric motor 5 to compress fluid from an inlet 6 as shown by an arrow 7 and guide it to a differential user 8 .
前記可変動翼１は、一体に設けた動翼ピボツト
９によりスラスト玉軸受１０を介して回転ハブ
２，３の外周に回転自在に取付けられており、且
つ動翼ピボツト９の内側端部にアーム１１を介し
てスライドシユー１２が設けられ、該スライドシ
ユー１２が前記回転ハブ２，３の内部に設けられ
たガイドリング１３，１４間のガイド溝１５に嵌
合されており、前記ガイドリング１３，１４を軸
中心線に沿う方向１６，１７に動かすことによ
り、前記可変動翼１のすべてを同時に同方向に同
角度回転１８させて調整することができるように
なつている。 The variable blade 1 is rotatably attached to the outer periphery of the rotary hubs 2 and 3 via a thrust ball bearing 10 by an integrally provided rotor blade pivot 9, and an arm is attached to the inner end of the rotor blade pivot 9. A slide shoe 12 is provided through the guide ring 11, and the slide shoe 12 is fitted into a guide groove 15 between guide rings 13 and 14 provided inside the rotating hubs 2 and 3. By moving the blades 13 and 14 in directions 16 and 17 along the axis center line, all of the variable blades 1 can be rotated 18 in the same direction and at the same angle for adjustment.
又前記回転ハブ２内には、一側が回転ハブ２に
固定され且つ他側が連結部材１９によつて前記ガ
イドリング１３に固定された制御シリンダ２０が
設けられている。制御シリンダ２０は制御ロツド
２１の移動に応じてその小さな操作力を大きな操
作力に変換するためのもので、制御シリンダ２０
にはパイロツト弁２２が設けられていると共に、
油圧装置２３に接続されたロータリージヨイント
２４を介して制御ロツド２１に連結されるように
なつており、前記制御ロツド２１を２５方向に移
動させると、油圧装置２３の油圧ポンプ２６から
の圧油が制御シリンダ２０のロツド側室２７に導
入されることにより制御シリンダ２０が縮小し、
よつてガイドリング１３及び連動ロツド２８を介
して前記制御シリンダ２０に連結したガイドリン
グ１４が16方向に増作動して可変動翼１の回動が
行われ、一方制御ロツド２１を29方向に移動させ
ると、圧油がシリンダヘツド側室３０に導入され
て制御シリンダ２０が伸長し、よつてガイドリン
グ１３，１４が17方向に増作動して可変動翼１が
前記と逆方向に回動するようになつている。尚、
図中３１は動翼ピボツト９に取付けたバランス調
整アームを示す。 Further, a control cylinder 20 is provided within the rotary hub 2 and is fixed on one side to the rotary hub 2 and on the other side to the guide ring 13 by a connecting member 19. The control cylinder 20 is for converting a small operating force into a large operating force according to the movement of the control rod 21.
is provided with a pilot valve 22, and
It is connected to the control rod 21 via a rotary joint 24 connected to the hydraulic device 23, and when the control rod 21 is moved in 25 directions, pressure oil from the hydraulic pump 26 of the hydraulic device 23 is released. is introduced into the rod side chamber 27 of the control cylinder 20, thereby causing the control cylinder 20 to contract.
Therefore, the guide ring 14 connected to the control cylinder 20 via the guide ring 13 and the interlocking rod 28 is actuated in 16 directions to rotate the variable blade 1, while the control rod 21 is moved in 29 directions. When this is done, pressure oil is introduced into the cylinder head side chamber 30 and the control cylinder 20 is extended, so that the guide rings 13 and 14 are actuated more in the 17 direction and the variable blade 1 is rotated in the opposite direction. It's getting old. still,
In the figure, numeral 31 indicates a balance adjustment arm attached to the rotor blade pivot 9.
前記構成において、制御ロツド２１の駆動制御
を行う場合、制御ロツド２１に作動レバー３２を
介しデイフユーザ８を貫通する制御軸３３を設
け、該制御軸３３の外端部に固設した制御レバー
３４を、連結ロツド３５を介し連結したコントロ
ールドライブ３６における駆動レバー３７の作動
により行つている。 In the above configuration, when controlling the drive of the control rod 21, the control rod 21 is provided with a control shaft 33 that passes through the differential user 8 via an operating lever 32, and a control lever 34 is fixedly attached to the outer end of the control shaft 33. , by actuation of a drive lever 37 in a control drive 36 connected via a connecting rod 35.
従つて、もし制御シリンダ２０が故障したよう
な場合でも、駆動レバー３７の作動力は制御レバ
ー３４を介し制御軸３３、制御ロツド２１、ロー
タリージヨイント２４、パイロツト弁２２等に作
用してしまうので、これら部材或いは機器に過ト
ルクが掛かり破損させてしまう虞を有していた。 Therefore, even if the control cylinder 20 breaks down, the operating force of the drive lever 37 will act on the control shaft 33, control rod 21, rotary joint 24, pilot valve 22, etc. via the control lever 34. However, there is a risk that excessive torque may be applied to these members or devices and cause them to be damaged.
即ち、一般に、前記の制御軸３３の如きトルク
被伝達軸を駆動するのに必要なトルクが経時的に
変化する場合、トルク被伝達軸が駆動されるまで
無制限にトルクを加えると、関連駆動部品が高荷
重のために破損や変形を起す危険をはらんでい
る。殊に、前記の制御シリンダ２０の如き、油圧
駆動機器のスプール弁を駆動する場合には、小さ
な駆動力で油圧により大きな駆動力を発生させる
ものであり、コントローラからスプール弁までは
大荷重が働かないので、特別に丈夫に設計する必
要はない。従つて、何らかの事故で油圧駆動機器
の油圧駆動能力が喪失すると、今まで油圧機器で
支持されていた反力が、場合によつてはスプール
弁や動力伝達機構及びコントローラに至り、高荷
重支持用に設計されていないこれらの部品を破損
に導くことになる。又油圧駆動機器が正常に機能
していても、駆動力がこの能力を超える場合にも
同様な結果を招く。 That is, in general, when the torque required to drive a torque-transmitted shaft such as the control shaft 33 changes over time, if torque is applied without limit until the torque-transmitted shaft is driven, the related drive components There is a risk of damage or deformation due to high loads. In particular, when driving a spool valve of a hydraulically driven device such as the control cylinder 20 described above, a large driving force is generated by hydraulic pressure with a small driving force, and a large load is applied from the controller to the spool valve. There is no need to design it to be particularly durable. Therefore, if the hydraulic drive capability of hydraulic drive equipment is lost due to some kind of accident, the reaction force that was previously supported by the hydraulic equipment may reach the spool valve, power transmission mechanism, and controller, causing the heavy load support This can lead to damage to these parts for which they were not designed. Even if the hydraulically driven equipment is functioning normally, similar results will occur if the driving force exceeds this capacity.
本発明は斯かる実情に鑑み、トルク被伝達軸以
降の関連部品に対し過大なトルクが伝達しないよ
うにした過トルク伝達防止用レバー装置を提供す
べく成したものである。 In view of the above circumstances, the present invention has been made in order to provide a lever device for preventing excessive torque transmission, which prevents excessive torque from being transmitted to related parts after the torque-transmitted shaft.
以下、図面を参照して本発明の実施例を説明す
る。 Embodiments of the present invention will be described below with reference to the drawings.
第４図及び第５図に示す如く、トルク被伝達軸
３８の端面にフランジ板３９を固着すると共に、
該フランジ板３９と平行にフランジ板４０を適宜
離隔配置し、且つ前記フランジ板３９の中心に支
持ピン４１を植設し、更にフランジ板３９，４０
間には、支持ピン４１を通る直線上の対称位置に
支持軸４２ａ，４２ｂを平行に取付ける。又、支
持点が二等辺三角形の各頂角部に配置された如き
ハンガー部材４３の二等辺にて形成される支持点
を、前記支持ピン４１に枢着し、他の２支持点に
所要張力のスプリング４４，４４引張コイルばね
の一端を夫々係止し、更に各スプリング４４，４
４の他端を、基端に前記支持軸４２ａ，４２ｂと
係合し得る円弧面４５，４５を有するボツクス型
トルク伝達レバー４６内に基端側より平行に挿入
して、該トルク伝達レバー４６の先端部にボルト
４７，４７止めし、以て該スプリング４４，４４
の張力によりトルク伝達レバー４６の円弧面４
５，４５を前記支持軸４２，４２に係合せしめ
る。 As shown in FIGS. 4 and 5, a flange plate 39 is fixed to the end surface of the torque-transmitted shaft 38, and
A flange plate 40 is arranged parallel to the flange plate 39 at an appropriate distance, and a support pin 41 is installed in the center of the flange plate 39.
In between, support shafts 42a and 42b are mounted parallel to each other at symmetrical positions on a straight line passing through the support pin 41. Further, a support point formed by the isosceles of the hanger member 43, in which the support point is arranged at each apex corner of an isosceles triangle, is pivoted to the support pin 41, and the other two support points are applied with the required tension. One end of each spring 44, 44 tension coil spring is locked, and each spring 44, 4
4 is inserted in parallel from the base end side into a box-type torque transmission lever 46 having arcuate surfaces 45, 45 at the base end that can engage with the support shafts 42a, 42b. Bolts 47, 47 are fixed to the tips of the springs 44, 44.
Due to the tension of the arc surface 4 of the torque transmission lever 46
5 and 45 are engaged with the support shafts 42 and 42.
今、第５図において、トルク伝達レバー４６に
矢印の方向にトルクMoが作用したとする。支持
軸４２ａ，４２ｂに働く抗力をRa，Rbとする
と、モーメントの釣合い式は次のようになる。 Now, in FIG. 5, it is assumed that a torque Mo acts on the torque transmission lever 46 in the direction of the arrow. Assuming that the drag forces acting on the support shafts 42a and 42b are Ra and Rb, the moment balance equation is as follows.
Mo＝Rbl1＋Ral1
但し、Rb＝Fs−１／２Mo／l1
Ra＝Fs−１／２Mo／l1
尚、１／２Mo／l1
：モーメントMoが加わつたことにより支持
軸４２ａ，４２ｂに付加又は減少する抗力
Fs：スプリング１本の張力
ここで、Raが常に正の値である抗力であれば、
トルク伝達レバー４６に加えられたMoはトルク
被伝達軸３８に伝えられる。そして伝達トルク
Moが徐々に大きくなり、Rbが大きくなる一方
Raが零若しくは負の領域になると、即ち、支持
軸４２ａとトルク伝達レバー４６との抗力が零若
しくは両者の間に隙間ができてしまうと、伝達ト
ルクMoは、
Mo＝Mmax＝Rbl1−０
＝（Fs＋１／２Mo／l1）l1
＝Fsl1＋１／２Mmax
∴Mmax＝2Fsl1
となり、トルク伝達レバー４６はMmax以上の
トルクをトルク被伝達軸３８に伝えず、トルク伝
達レバー４６は支持軸４２ｂを支点にリリースす
る（第６図参照）。この際、スプリング４４，４
４の伸びは初期と殆ど差がない（リリース後も
Fsの値に殆ど変化はない）ので、本装置は、装
置寸法であるl1とスプリング張力Fsとで決まる一
定トルクを超える伝達トルクをリリースする機能
を有する。 Mo=Rbl 1 +Ral 1 However, Rb=Fs-1/2Mo/l 1 Ra=Fs-1/2Mo/l 1 Furthermore, 1/2Mo/l 1 : Due to the moment Mo added, the support shafts 42a and 42b Added or decreased drag force Fs: Tension of one spring Here, if Ra is always a positive value, then
Mo applied to the torque transmission lever 46 is transmitted to the torque transmitted shaft 38. and transmission torque
While Mo gradually increases and Rb increases
When Ra becomes zero or in a negative region, that is, when the resistance between the support shaft 42a and the torque transmission lever 46 is zero or a gap is created between the two, the transmission torque Mo is: Mo=Mmax=Rbl 1 −0 =(Fs+1/2Mo/l 1 )l 1 =Fsl 1 +1/2Mmax ∴Mmax=2Fsl 1 , the torque transmission lever 46 does not transmit torque greater than Mmax to the torque transmitted shaft 38, and the torque transmission lever 46 is connected to the support shaft. Release using 42b as a fulcrum (see Figure 6). At this time, the springs 44, 4
There is almost no difference in the growth of 4 from the initial stage (even after release)
(There is almost no change in the value of Fs) Therefore, this device has a function of releasing the transmitted torque exceeding a constant torque determined by the device dimension l 1 and the spring tension Fs.
また、同様に、第５図において、トルクMoと
反対方向のトルクに対してトルク伝達レバー４６
は、支持軸４２ａを支点として過大なトルクをリ
リースする。 Similarly, in FIG. 5, the torque transmission lever 46 is
releases excessive torque using the support shaft 42a as a fulcrum.
従つて、第１図及び第２図で示した制御軸３３
と制御レバー３４の代りに、本装置を用いれば、
制御軸３３以降の関連部品に対し過大なトルクが
伝達しない。 Therefore, the control shaft 33 shown in FIGS.
If this device is used instead of the control lever 34,
Excessive torque is not transmitted to related parts after the control shaft 33.
尚、本発明は前記実施例のみに限定されるもの
ではなく、本発明の要旨を逸脱しない限り種種変
更を加え得ることは勿論である。 It should be noted that the present invention is not limited to the above embodiments, and it goes without saying that various changes can be made without departing from the gist of the present invention.
以上説明したように本発明の過トルク伝達防止
用レバー装置によれば、トルク被伝達軸の正逆両
回転方向のいずれか一方に一定以上のトルクが作
用すると、トルク伝達レバーが自動的にリリース
して作動トルクを一定値以下に制御し得るので、
トルク被伝達軸に連絡する関連部品の破損を防止
することができる。又、本装置は、作動トルクに
よつてスプリングの伸縮現象を応用する方式では
なく、スプリングの張力は作動トルクに関係なく
初期張力が保たれるので、リリーストルクを設定
し易く、且つこの設定には経時的劣化も起らな
い。 As explained above, according to the overtorque transmission prevention lever device of the present invention, when a torque of a certain level or more is applied to either the forward or reverse rotation direction of the torque transmitted shaft, the torque transmission lever is automatically released. The operating torque can be controlled below a certain value by
Damage to related parts connected to the torque-transmitted shaft can be prevented. In addition, this device does not apply the expansion and contraction phenomenon of the spring depending on the operating torque, but the initial tension of the spring is maintained regardless of the operating torque, so it is easy to set the release torque, and it is easy to set the release torque. No deterioration occurs over time.
第１図はトルク伝達レバーを備えた可変動翼軸
流フアンの一般的な構成例を示す側面図、第２図
は第１図の可変動翼の作動機構を示す斜視図、第
３図は制御シリンダ付近の詳細を示す切断側面
図、第４図は本発明の過トルク伝達防止用レバー
装置の分解斜視図、第５図は第４図の−矢視
に相当する組立図、第６図は作動状態を示す説明
図である。
３８…トルク被伝達軸、４１…支持ピン、４２
ａ，４２ｂ…支持軸、４３…ハンガー部材、４４
…スプリング（引張コイルばね）、４５…円弧面、
４６…トルク伝達レバー。
Figure 1 is a side view showing a general configuration example of a variable blade axial flow fan equipped with a torque transmission lever, Figure 2 is a perspective view showing the operating mechanism of the variable blade shown in Figure 1, and Figure 3 is a 4 is an exploded perspective view of the lever device for preventing overtorque transmission of the present invention; FIG. 5 is an assembled view corresponding to the - arrow direction in FIG. 4; FIG. 6 is a cutaway side view showing details of the vicinity of the control cylinder; is an explanatory diagram showing an operating state. 38...Torque transmitted shaft, 41...Support pin, 42
a, 42b...support shaft, 43...hanger member, 44
...Spring (tension coil spring), 45...Circular surface,
46...Torque transmission lever.
Claims (1)
支持ピンを挟んだ対称位置に２本１対の支持軸を
夫々設け、前記支持ピンにハンガー部材を枢着
し、前記支持軸に、トルク伝達レバーの基端面に
支持軸と対応するように形成した円弧面を当接さ
せると共に、前記トルク伝達レバーの先端部と前
記ハンガー部材との間に引張コイルばねを張設し
たことを特徴とする過トルク伝達防止用レバー装
置。1. A support pin is provided at the center of the end surface of the torque-transmitted shaft, and a pair of support shafts are provided at symmetrical positions across the support pin, a hanger member is pivotally attached to the support pin, and the torque is transmitted to the support shaft. A circular arc surface formed to correspond to the support shaft is brought into contact with the base end surface of the transmission lever, and a tension coil spring is stretched between the tip of the torque transmission lever and the hanger member. Lever device for preventing excessive torque transmission.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22770483A JPS60121358A (en) | 1983-12-01 | 1983-12-01 | Lever device for preventing transmission of overtorque |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22770483A JPS60121358A (en) | 1983-12-01 | 1983-12-01 | Lever device for preventing transmission of overtorque |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60121358A JPS60121358A (en) | 1985-06-28 |
| JPH0227543B2 true JPH0227543B2 (en) | 1990-06-18 |
Family
ID=16865038
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP22770483A Granted JPS60121358A (en) | 1983-12-01 | 1983-12-01 | Lever device for preventing transmission of overtorque |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60121358A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0437004Y2 (en) * | 1985-10-29 | 1992-09-01 | ||
| JP4583546B2 (en) * | 2000-04-13 | 2010-11-17 | 三菱重工コンプレッサ株式会社 | Centrifugal compressor |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5754798Y2 (en) * | 1978-09-08 | 1982-11-26 |
-
1983
- 1983-12-01 JP JP22770483A patent/JPS60121358A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS60121358A (en) | 1985-06-28 |
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