JPH0314094B2 - - Google Patents
Info
- Publication number
- JPH0314094B2 JPH0314094B2 JP14119185A JP14119185A JPH0314094B2 JP H0314094 B2 JPH0314094 B2 JP H0314094B2 JP 14119185 A JP14119185 A JP 14119185A JP 14119185 A JP14119185 A JP 14119185A JP H0314094 B2 JPH0314094 B2 JP H0314094B2
- Authority
- JP
- Japan
- Prior art keywords
- spring
- mounting plate
- seat plate
- plate
- leaf spring
- 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
Links
- 239000006096 absorbing agent Substances 0.000 claims description 9
- 238000005452 bending Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000005284 excitation Effects 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F7/00—Vibration-dampers; Shock-absorbers
- F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
- F16F7/104—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted
- F16F7/116—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted on metal springs
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
Description
【発明の詳細な説明】
この発明は振子バネ式の動吸振器に関するもの
である。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a pendulum spring type dynamic vibration absorber.
振子バネ式の動吸振器においては、大きなエネ
ルギを吸収させるため、一般に振子の振幅が大き
いので、使用するバネに対して特別の考慮が必要
である。即ち長時間の使用に対しても疲労しない
ように応力を小さくすること。また一方バネ定数
も或る程度の大きさを有することが必要である。
更に起振力の角振動数に対応して動吸振器の固有
振動数を容易に調整できることが必要である。し
かし従来これらの要求をすべて充足できるような
動吸振器は見当らない。 In a pendulum spring type dynamic vibration absorber, the amplitude of the pendulum is generally large in order to absorb a large amount of energy, so special consideration must be given to the spring used. In other words, the stress must be reduced so that fatigue does not occur even during long-term use. On the other hand, it is also necessary that the spring constant has a certain degree of magnitude.
Furthermore, it is necessary to be able to easily adjust the natural frequency of the dynamic vibration damper in accordance with the angular frequency of the excitation force. However, no dynamic vibration absorber has hitherto been found that can satisfy all of these requirements.
この発明は上記の要求を充足できるようにした
動吸振器を提供することを目的とするものであ
る。 The object of the present invention is to provide a dynamic vibration absorber that can satisfy the above requirements.
この発明の動吸振器は、枠体内の中心部に座板
を揺動自在に設け、この座板の中央部にバネ取付
板を垂設すると共に、このバネ取付板を挟んで一
対の重錘を上下動可能に吊下げ、且つ上記バネ取
付板に一対のＵ形板バネの一端を上記座板の揺動
支点に近接させて取付けると共に、他端を上記一
端より下方の位置で上記枠体内壁に固着してなる
ものである。 The dynamic vibration absorber of the present invention has a seat plate swingably provided at the center of the frame, a spring mounting plate vertically disposed at the center of the seat plate, and a pair of weights sandwiching the spring mounting plate. is suspended in a vertically movable manner, and one end of a pair of U-shaped leaf springs is attached to the spring mounting plate in close proximity to the swing fulcrum of the seat plate, and the other end is placed within the frame at a position below the one end. It is fixed to the wall.
以下この発明の一実施例を図面により説明す
る。円筒状枠体１の天板１ａの中心線上に軸３用
の１組の軸受２，２が設けられている。矩形状座
板４に設けられた１組のピローブロツク５，５を
上記軸３に係合させて、座板４は軸３に対し揺動
できるようになつている。座板４と下座板６との
間は、重錘１０を上下に案内する複数本の案内棒
９を介して連結されている。そして座板４と下座
板６との間にバネ取付板７が設けられると共に、
このバネ取付板７を挟んで設けられた１対の重錘
１０，１０を上下させるためのねじ棒１１，１１
が取付けられている。そして重錘１０はねじ棒１
１に螺合する上下のナツト１２，１２を緩め、案
内棒９に沿つて上下に移動後、ナツト１２，１２
を締め付けることによつて上下に位置調整できる
ようになつている。また断面Ｕ形の板バネ８，８
が、その１端を取付板７に取付け、他端を枠体１
の内壁に固着して、取付板に対して対称に設けら
れている。この場合取付板７への取付点８ａは取
付板の揺動軸３に隣接させてあり、一方枠体内壁
への固着点８ｂは、上記取付点８ａより下方に位
置させてある。即ち揺動軸３から取付点８ａまで
の距離l1に対し、固着点８ｂまでの距離l2は大き
くなつている。 An embodiment of the present invention will be described below with reference to the drawings. A pair of bearings 2, 2 for the shaft 3 is provided on the center line of the top plate 1a of the cylindrical frame 1. A pair of pillow blocks 5, 5 provided on the rectangular seat plate 4 are engaged with the shaft 3, so that the seat plate 4 can swing relative to the shaft 3. The seat plate 4 and the lower seat plate 6 are connected via a plurality of guide rods 9 that guide the weight 10 up and down. A spring mounting plate 7 is provided between the seat plate 4 and the lower seat plate 6, and
Threaded rods 11, 11 for raising and lowering a pair of weights 10, 10 provided with this spring mounting plate 7 in between.
is installed. And the weight 10 is a threaded rod 1
Loosen the upper and lower nuts 12, 12 that are screwed into
The position can be adjusted up and down by tightening. In addition, leaf springs 8, 8 having a U-shaped cross section
, one end is attached to the mounting plate 7, and the other end is attached to the frame 1.
It is fixed to the inner wall of the mounting plate and is symmetrically provided with respect to the mounting plate. In this case, the attachment point 8a to the attachment plate 7 is located adjacent to the pivot axis 3 of the attachment plate, while the attachment point 8b to the inner wall of the frame is located below the attachment point 8a. That is, the distance l 2 from the swing shaft 3 to the attachment point 8b is larger than the distance l 1 from the swing shaft 3 to the attachment point 8a.
上記の構成により、重錘１０を上下して、揺動
軸３から重錘１０の重心までの長さｌを変えるこ
とにより、動吸振器の固有振動数を変えることが
できる。また起振力の角振動数の変動に対応させ
るため質量比を大きくすべく重錘の質量を大きく
した場合にも、これを２分割して２個の重錘１
０，１０とすることにより個々の重錘の質量を半
減して、位置調整が容易にできるようになつてい
る。 With the above configuration, the natural frequency of the dynamic vibration absorber can be changed by moving the weight 10 up and down and changing the length l from the swing axis 3 to the center of gravity of the weight 10. Also, when the mass of the weight is increased to increase the mass ratio in order to cope with fluctuations in the angular frequency of the excitation force, it can be divided into two and the two weights 1
By setting the weights to 0 and 10, the mass of each weight can be halved and the position can be easily adjusted.
また重錘１０が大きく振れた場合にも取付点８
ａの振動軸３からの距離l1が小さいので、板バネ
８の変位を小さくすることができる。これにより
板バネに作用する応力を小さくすることができ
る。また、重錘１０の振れに伴い取付点８ａで、
板バネ８に押圧力Ｐが作用し、また板バネ８の変
形に伴い取付点８ａで取付板７の方向に力が作用
し、その反力P′が板バネ８に作用する。 Also, if the weight 10 swings significantly, the attachment point 8
Since the distance l 1 of a from the vibration axis 3 is small, the displacement of the leaf spring 8 can be made small. This allows the stress acting on the leaf spring to be reduced. Also, due to the swing of the weight 10, at the attachment point 8a,
A pressing force P acts on the leaf spring 8, and as the leaf spring 8 deforms, a force acts in the direction of the mounting plate 7 at the attachment point 8a, and a reaction force P' acts on the leaf spring 8.
そして、板バネ８の屈曲点Ａにおける曲率半径
をｒ、吊下軸側の板バネ８の直線部分の長さつま
り取付点８ａから８ｃまでの距離をl3、枠体内壁
側の板バネ８の直線部分の長さつまり８ｂから８
ｄまでの距離をl4とすると、屈曲点Ａにおいて板
バネ８に作用する曲げモーメントMAは、MA＝Ｐ
（l3＋ｒ）−P′rとなり、応力σA＝MA・ｔ／２／Ｉ
となる。ここで、ｔは板バネ８の厚さである。第
４図に横軸にl3／ｒ、縦軸にl4／ｒを取り、応力
σAが一定の点を実線で、またバネ定数ｋが一定の
点を破線で示す。図上で交点ととでは、バネ
定数ｋは等しいが、応力σAはの方が、より小
さくなつている。このことは、バネ定数が等しい
Ｕ形板バネの場合、l3を大きく、l4を小さく、即
ちl1＜l2としたときは、板バネ８に作用する応力
を更に小さくすることができる。一方取付点位置
を、重錘１０の位置即ちｌとしたときの所要バネ
定数をkeqとすると、取付点位置をl1とした場合
のバネ定数ｋはｋ＝keq（ｌ／l1）2とする必要があ
るが、これは板バネ８の幅を大きくすることによ
り対処することができる。 Then, the radius of curvature at the bending point A of the leaf spring 8 is r, the length of the straight part of the leaf spring 8 on the hanging shaft side, that is, the distance from the attachment points 8a to 8c is l 3 , and the leaf spring 8 on the wall side of the frame The length of the straight line part, that is, 8b to 8
If the distance to d is l 4 , the bending moment M A acting on the leaf spring 8 at the bending point A is M A = P
(l 3 +r)−P′r, stress σ A =M A・t/2/I
becomes. Here, t is the thickness of the leaf spring 8. In FIG. 4, l 3 /r is plotted on the horizontal axis and l 4 /r is plotted on the vertical axis, and points where the stress σ A is constant are shown by solid lines, and points where the spring constant k is constant are shown by broken lines. In the diagram, the spring constant k is the same at the intersection, but the stress σ A is smaller at the intersection. This means that in the case of U-shaped leaf springs with the same spring constant, when l 3 is large and l 4 is small, that is, l 1 < l 2 , the stress acting on the leaf spring 8 can be further reduced. . On the other hand, if the required spring constant is keq when the attachment point position is the position of the weight 10, ie l, then the spring constant k when the attachment point position is l1 is k=keq(l/l1) 2 . However, this can be dealt with by increasing the width of the leaf spring 8.
なお、座板４と天板１ａとの間に、揺動軸３に
対し対称にダンパーを配設することにより、最適
減衰を得ることができる。また取付点８ａにおけ
る板バネ８の支持をピン支持構造にすることによ
り板バネ８に作用する応力を緩和することができ
る。 Note that optimal damping can be obtained by disposing a damper symmetrically with respect to the swing axis 3 between the seat plate 4 and the top plate 1a. Further, by supporting the plate spring 8 at the attachment point 8a using a pin support structure, the stress acting on the plate spring 8 can be alleviated.
この発明の動吸振器は上記のようなもので、動
吸振器の固有振動数を容易に調整することがで
き、また所要のバネ定数を持つと共に、板バネに
作用する応力を小さくすることができる。 The dynamic vibration absorber of the present invention is as described above, and can easily adjust the natural frequency of the dynamic vibration absorber, have the required spring constant, and reduce the stress acting on the leaf spring. can.
第１図は本発明の一実施例を枠体を縦した状態
で示す側面図、第２図は第１図の−線矢視
図、第３図は板バネの配設状態の説明図、第４図
は横軸にl3／ｒ、縦軸にl4／ｒを取つた場合の板
バネの応力σAとバネ定数ｋとの関係を示す説明図
である。
１……枠体、４……座板、７……バネ取付板、
８……Ｕ形板バネ、１０……重錘。
FIG. 1 is a side view showing an embodiment of the present invention with the frame in a vertical position, FIG. 2 is a view taken along the - line in FIG. 1, and FIG. 3 is an explanatory diagram of the arrangement of leaf springs. FIG. 4 is an explanatory diagram showing the relationship between the stress σ A of the leaf spring and the spring constant k when l 3 /r is plotted on the horizontal axis and l 4 /r is plotted on the vertical axis. 1...Frame body, 4...Seat plate, 7...Spring mounting plate,
8... U-shaped leaf spring, 10... Weight.
Claims (1)
の座板の中央部にバネ取付板を垂設すると共に、
このバネ取付板を挟んで一対の重錘を上下動可能
に吊下げ、且つ上記板バネ取付板に一対のＵ形板
バネの一端を対称に上記座板の揺動支点に近接さ
せて取付けると共に、他端を上記一端より下方の
位置で上記枠体内壁に固着してなる動吸振器。1. A seat plate is swingably provided in the center of the frame, and a spring mounting plate is vertically installed in the center of the seat plate,
A pair of weights are suspended vertically movably across the spring mounting plate, and one end of the pair of U-shaped leaf springs is mounted symmetrically close to the swing fulcrum of the seat plate on the leaf spring mounting plate. , a dynamic vibration absorber having the other end fixed to the inner wall of the frame at a position below the one end.
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14119185A JPS622033A (en) | 1985-06-27 | 1985-06-27 | Dynamic vibration damper |
| US06/874,486 US4700817A (en) | 1985-06-27 | 1986-06-16 | Dynamic vibration absorber with spring-supported pendulum |
| KR1019860004812A KR910000561B1 (en) | 1985-06-27 | 1986-06-17 | Dynamic vibration absorber with spring-supported pendulum |
| FI862744A FI82758C (en) | 1985-06-27 | 1986-06-26 | Dynamic vibration damper |
| DE8686108762T DE3666612D1 (en) | 1985-06-27 | 1986-06-27 | Dynamic vibration absorber with spring-supported pendulum |
| EP86108762A EP0206348B1 (en) | 1985-06-27 | 1986-06-27 | Dynamic vibration absorber with spring-supported pendulum |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14119185A JPS622033A (en) | 1985-06-27 | 1985-06-27 | Dynamic vibration damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS622033A JPS622033A (en) | 1987-01-08 |
| JPH0314094B2 true JPH0314094B2 (en) | 1991-02-26 |
Family
ID=15286276
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP14119185A Granted JPS622033A (en) | 1985-06-27 | 1985-06-27 | Dynamic vibration damper |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS622033A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6029496A (en) * | 1983-07-27 | 1985-02-14 | Mazda Motor Corp | Method for drying car body after chemical conversion treatment |
| JPS63243544A (en) * | 1987-03-27 | 1988-10-11 | Nkk Corp | Control device for dynamic vibration reducer |
| JP6087566B2 (en) * | 2012-10-03 | 2017-03-01 | 株式会社荏原製作所 | Pump device having dynamic vibration absorber |
| EP4115095A1 (en) * | 2020-03-03 | 2023-01-11 | FM Energie GmbH & Co. KG | Frequency-adaptive leaf-spring tuned mass damper |
-
1985
- 1985-06-27 JP JP14119185A patent/JPS622033A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS622033A (en) | 1987-01-08 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| LAPS | Cancellation because of no payment of annual fees |