JPH03219131A - Rotary damper - Google Patents
Rotary damperInfo
- Publication number
- JPH03219131A JPH03219131A JP1120890A JP1120890A JPH03219131A JP H03219131 A JPH03219131 A JP H03219131A JP 1120890 A JP1120890 A JP 1120890A JP 1120890 A JP1120890 A JP 1120890A JP H03219131 A JPH03219131 A JP H03219131A
- Authority
- JP
- Japan
- Prior art keywords
- oil
- oil chamber
- damping force
- housing
- chamber
- 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.)
- Granted
Links
- 238000013016 damping Methods 0.000 claims abstract description 51
- 230000007246 mechanism Effects 0.000 claims abstract description 21
- 239000007788 liquid Substances 0.000 claims description 5
- 239000012530 fluid Substances 0.000 claims description 3
- 230000001105 regulatory effect Effects 0.000 abstract description 5
- 230000007423 decrease Effects 0.000 abstract description 3
- 230000003247 decreasing effect Effects 0.000 abstract 2
- 241001417494 Sciaenidae Species 0.000 description 4
- 238000005192 partition Methods 0.000 description 4
- 238000007789 sealing Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000003381 stabilizer Substances 0.000 description 1
- 229920003002 synthetic resin Polymers 0.000 description 1
- 239000000057 synthetic resin Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Landscapes
- Fluid-Damping Devices (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は、回転方向ての緩衝を行なうためのロータリー
タンパ−に関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a rotary tamper for providing damping in the rotational direction.
（従来の技術）
従来、ロータリーダンパーとしては、たとえば、特開昭
６４−１２１５２号公報て開示されたものがある。(Prior Art) Conventionally, as a rotary damper, there is one disclosed, for example, in Japanese Patent Application Laid-Open No. 12152/1983.
これは、第５図および第６図に示すように、ハウジング
ｌ内にベアリング２により回転可能に支持された中空軸
３か貫通し、中空軸３には径方向外側に向かって延びハ
ウジング１の内周面に摺接する可動ベーン４か一体的に
設けられている。また、ハウジングｌには、径方向内側
に向かって延び中空軸３の外周面に摺接する固定ヘーン
５か一体的に設けられている。そして、これら可動ベー
ン４および固定ベーン５により第１の外側油室６と第２
の外側油室７とか画成されている。一方、中空軸３は、
内部を隔壁８によって左右の室に分離され、左側の室は
、セパレータ９により第１の内側油室１０と第２の内側
油室１．１とに画成されていて、第１の内側油室ｌＯは
第１の外側油室６と油孔１２により連通され、第２の内
側油室１１は第２の外側油室７と油孔１３により連通さ
れている。As shown in FIGS. 5 and 6, a hollow shaft 3 rotatably supported by a bearing 2 passes through the housing 1, and extends radially outward from the housing 1. A movable vane 4 that slides on the inner circumferential surface is integrally provided. Furthermore, a fixed vane 5 that extends radially inward and slides into contact with the outer circumferential surface of the hollow shaft 3 is integrally provided in the housing l. These movable vanes 4 and fixed vanes 5 create a first outer oil chamber 6 and a second outer oil chamber.
An outer oil chamber 7 is defined. On the other hand, the hollow shaft 3 is
The interior is divided into left and right chambers by a partition wall 8, and the left chamber is defined by a separator 9 into a first inner oil chamber 10 and a second inner oil chamber 1.1. The chamber lO communicates with the first outer oil chamber 6 through an oil hole 12, and the second inner oil chamber 11 communicates with the second outer oil chamber 7 through an oil hole 13.
セパレータ９には第１の内側油室１０と第２の内側油室
１１を連通ずる複数の油路１４，１５か形成されており
、セパレータ９の両面には、第１の内側油室１０から第
２の内側油室１１へ油路１４を通って油液か流れるとき
に減衰力を発生するディスクハルツ１６と第２の内側油
室１１から第１の内側油室１０へ油路１５を通って油液
か流れるときに減衰力を発生するディスクバルブ１７と
かそれぞれ配置されている。A plurality of oil passages 14 and 15 are formed in the separator 9 to communicate between the first inner oil chamber 10 and the second inner oil chamber 11. The oil passes through the oil passage 14 to the second inner oil chamber 11 and the disc HURZ 16 that generates a damping force when it flows, and the oil passage 15 from the second inner oil chamber 11 to the first inner oil chamber 10. A disc valve 17 that generates a damping force when oil flows is arranged in each case.
隔壁８により画成された右側の室は回転軸３の軸方向に
延長して設けられており、内部にはフリーピストン１８
か摺動自在に配置されていて、フリーピストン１８と隔
壁８の間の室は前記外側の油室６，７と連通され、フリ
ーピストン１８の隔壁８と反対側には高圧ガスか封入さ
れた高圧ガス室１９か構成されている。A right-hand chamber defined by the partition wall 8 is provided extending in the axial direction of the rotating shaft 3, and a free piston 18 is provided inside.
The chamber between the free piston 18 and the partition wall 8 communicates with the outer oil chambers 6 and 7, and the side of the free piston 18 opposite to the partition wall 8 is filled with high-pressure gas. A high pressure gas chamber 19 is also configured.
以上の構成によれば、中空軸３か第１の外側の油室６の
容積を減少させる方向に回転すると、第１の外側油室６
内の油液か油孔１２を通りて第１の内側油室１０に流入
し、流入した油液はセパレータ９に形成された油路１４
を通ってディスクハルツ１６を押し開けて第２の内側油
室１１に流入する。また、第２の内側油室１１に流入し
た油液は油孔１３を通って第２の外側油室７内に流入す
る。このときに油液かディスクハルツ１６を押し開いて
流れる際に減衰力が発生される。また、中空軸３が逆方
向に回転する場合は油液の流れる方向か逆となるたけて
同様の作用となる。According to the above configuration, when the hollow shaft 3 rotates in a direction that reduces the volume of the first outer oil chamber 6, the first outer oil chamber 6
The oil inside flows into the first inner oil chamber 10 through the oil hole 12, and the oil that flows in flows into the oil passage 14 formed in the separator 9.
The oil passes through the disk, pushes open the disc hearth 16, and flows into the second inner oil chamber 11. Further, the oil that has flowed into the second inner oil chamber 11 flows into the second outer oil chamber 7 through the oil hole 13 . At this time, a damping force is generated when the oil fluid pushes open the disc hearth 16 and flows. Furthermore, when the hollow shaft 3 rotates in the opposite direction, the same effect will occur since the direction in which the oil flows is reversed.
なお、フリーピストン１８は、温度によって油液か膨張
または収縮したときや、油液の漏れが生したときに適宜
移動して油液の体積補償をするものである。The free piston 18 moves appropriately to compensate for the volume of the oil when the oil expands or contracts due to temperature or when oil leaks.
（発明か解決しようとする課題）
しかしながら、上記従来のロータリータンバーては中空
軸３内部をセパレータ９により二つの内側油室１０．１
１に区画して、油室１０，１１間て生じる油液の流れに
よってディスクバルブ１６．１７を押し開いて減衰力を
発生するようにしたため次のような問題点を有していた
。(Problem to be solved by the invention) However, in the conventional rotary tambour described above, the inside of the hollow shaft 3 is separated by a separator 9 into two inner oil chambers 10.1.
1, and the disc valves 16 and 17 are pushed open by the flow of oil generated between the oil chambers 10 and 11 to generate a damping force, which has the following problems.
中空軸３内に油室１０，１１と減衰力を発生するディス
クハルツ１６．１７を設けているため、中空軸か太くな
ってしまい、ロータリータンバー全体か大型化してしま
うという問題点かあった。Since the oil chambers 10, 11 and the disc hartz 16, 17 that generate damping force are provided in the hollow shaft 3, the hollow shaft becomes thick, which causes the problem that the rotary tambour as a whole becomes large.
また、減衰力を発生するディスクハルツ１６．１７の外
径寸法も中空軸３の内径寸法により制限されてしまうた
め、減衰力特性の設定の自由度か小さいという問題点も
あった。Furthermore, since the outer diameter of the disk hartz 16, 17 that generates the damping force is also limited by the inner diameter of the hollow shaft 3, there is also a problem that the degree of freedom in setting the damping force characteristics is small.
さらに、中空軸３内の狭い空間内にセパレータ９やディ
スクバルブ１６．１７を組付なければならず、組付性も
悪いという問題点もあった。Furthermore, the separator 9 and the disc valves 16 and 17 must be assembled in a narrow space within the hollow shaft 3, resulting in poor assembly performance.
本発明、以上の問題点に鑑みてなされたもので、その目
的とするところは、大型化することかなく減衰力の設定
の自由度を高くてきかつ組付性の良いロータリータンバ
ーを提供することにある。The present invention has been made in view of the above-mentioned problems, and its purpose is to provide a rotary tambour that allows a high degree of freedom in setting damping force without increasing the size and is easy to assemble. It is in.
（課題を解決するための手段）
本発明のロータリータンバーは、油液か充満されたハウ
ジングと該ハウジングに回転可能に設けた回転軸との間
に、ハウジングに取付けた一以上の固定ベーンと回転軸
に取付けた一以上の可動ベーンとを該回転軸の周回り方
向に配置して複数の油室を画成し、ハウジングにおける
回転軸の軸方向の端部に調整油室を形成し、該調整油室
と前記各油室とを通路て連通させ、該通路に、油室から
調整油室への油液の流動により減衰力を発生する減衰力
発生機構を設け、ハウジングと回転軸との間の相対回転
時に、容積の小さくなる油室から減衰力発生機構及び調
整油室を介して容積の大きくなる油室へ油液か流動する
ように前記通路を構成してなるものである。(Means for Solving the Problems) The rotary tambour of the present invention has one or more fixed vanes attached to the housing and a rotating shaft between a housing filled with oil and a rotary shaft rotatably provided in the housing. One or more movable vanes attached to the shaft are arranged in the circumferential direction of the rotating shaft to define a plurality of oil chambers, and an adjustment oil chamber is formed at an end in the axial direction of the rotating shaft in the housing. The adjustment oil chamber and each of the oil chambers are communicated through a passage, and a damping force generation mechanism is provided in the passage to generate a damping force by the flow of oil from the oil chamber to the adjustment oil chamber. The passage is configured such that during relative rotation between the two, oil flows from the oil chamber whose volume decreases to the oil chamber whose volume increases via the damping force generation mechanism and the adjustment oil chamber.
また、油液か充満されたハウジングと該ハウジングに回
転可能に設けた回転軸との間に、ハウジングに取付けた
一以上の固定ベーンと回転軸に取付けた一以上の可動ベ
ーンとを該回転軸の周回り方向に配置して複数の油室を
画成し、ハウジングにおける回転軸の軸方向の端部に調
整油室を形成し、該調整油室と前記各油室とを二つずつ
の通路て連通させ、一方の通路に、油室から調整油室へ
の油液の流動により減衰力を発生する減衰力発生機構を
設け、他方の通路に、調整油室から油室への油液の流動
のみを許容する逆止弁を設けてなるものである。Further, between the housing filled with oil and a rotating shaft rotatably provided on the housing, one or more fixed vanes attached to the housing and one or more movable vanes attached to the rotating shaft are connected to the rotating shaft. A plurality of oil chambers are arranged in the circumferential direction of the housing, and an adjustment oil chamber is formed at the end of the housing in the axial direction of the rotating shaft, and the adjustment oil chamber and each of the oil chambers are separated into two oil chambers. One passage is provided with a damping force generation mechanism that generates damping force by the flow of oil from the oil chamber to the adjustment oil chamber, and the other passage is provided with a damping force generation mechanism that generates damping force by the flow of oil from the adjustment oil chamber to the oil chamber. The device is equipped with a check valve that allows only the flow of water.
（作用）
以上の構成とすると、ハウジングにおける回転軸の軸方
向の端部に調整油室を形成して減衰力発生機構を設けた
ため、従来よりも回転軸の径を細くすることかできると
ともに、従来のロータリータンパ−と同一の外径てあっ
ても油室の容積が大きくとれるため、作動流量を多くし
て大きな減衰力を発生させることが可能となる。また、
減衰力発生機構の外径寸法も自由に設定てきるため、発
生する減衰力特性の設定の自由度を高めることかてきる
。さらに、減衰力発生機構を狭い場所に組み付けること
もないため組付性の向上か図れる。(Function) With the above configuration, since the adjustment oil chamber is formed at the axial end of the rotating shaft in the housing and the damping force generation mechanism is provided, the diameter of the rotating shaft can be made smaller than before, and Even though the outer diameter is the same as that of a conventional rotary tamper, the volume of the oil chamber can be increased, so it is possible to increase the operating flow rate and generate a large damping force. Also,
Since the outer diameter dimension of the damping force generation mechanism can also be freely set, the degree of freedom in setting the generated damping force characteristics can be increased. Furthermore, since the damping force generating mechanism does not need to be assembled in a narrow space, ease of assembly can be improved.
（実施例）
つぎに、本発明の実施例を第１図および第２図に基づい
て説明する。(Example) Next, an example of the present invention will be described based on FIGS. 1 and 2.
ハウジング２０は、シリンダ部２１と、シリンダ部２Ｉ
の一端側に配置され、回転軸２２の一端側を回転可能に
支持するガイド部２３と、シリンダ部２Ｉの他端側な閉
塞するキャップ部２４と、シリンダ部２１とキャップ部
２４との間に設けられ回転軸２２の他端側を回転可能に
支持するハルツリテーナ２５と、か組み合わされてボル
ト２５によって固定されている。そして、ハウジング２
０内には油液か充満されている。The housing 20 includes a cylinder portion 21 and a cylinder portion 2I.
A guide part 23 that is arranged at one end and rotatably supports one end of the rotating shaft 22, a cap part 24 that closes the other end of the cylinder part 2I, and a space between the cylinder part 21 and the cap part 24. It is fixed by bolts 25 in combination with a Harutz retainer 25 that is provided and rotatably supports the other end of the rotating shaft 22 . And housing 2
0 is filled with oil.
ハウジング２０のシリンタ部２１内周側には、径方向内
側に延びて回転軸２２の外周面に摺接する固定ベーン２
７か回転軸２２の周回り方向て均等な角度をもって４個
所に取付けられており、回転軸２２には、径方向外側に
延びてシリンダ部２１の内周面に摺接する可動ベーン２
８か回転軸２２の周回り方向て均等な角度をもって４個
所に取付けられており、固定ヘーン２７と可動ベーン２
８とは交互に配設されている。そして、シリンダ部２１
と回転軸２２との間は、固定ベーン２７と可動ベーン２
８とて区画され複数の油室２９Ａ、２９Ｂが画成される
。A fixed vane 2 is provided on the inner peripheral side of the cylinder portion 21 of the housing 20 and extends radially inward and slides into contact with the outer peripheral surface of the rotating shaft 22.
Movable vanes 2 are attached to the rotary shaft 22 at four equal angles in the circumferential direction of the rotating shaft 22, and the movable vanes 2 extend radially outward and slide into contact with the inner circumferential surface of the cylinder portion 21.
The fixed vane 27 and the movable vane 2
8 are arranged alternately. And the cylinder part 21
A fixed vane 27 and a movable vane 2 are connected between the rotary shaft 22 and the rotary shaft 22.
A plurality of oil chambers 29A and 29B are defined.
ここて、各油室２９Ａ、２９Ｂを密封するシール構造の
一例を示す。第３図に示すように、可動ベーン２８の両
側面と先端面に溝２８ａ、２８ｂを形成し、各溝２８ａ
、２８ｂに板状のばね３０，３１を挿入して、可動ベー
ン２８の先端側には断面凹字形状のシール部材３２を摺
動自在に嵌合させ、側面の溝２８ｂにはＬ字形状のシー
ル部材３３を摺動自在に嵌め込んたものである。そして
、ばね３０によりシール部材３２をシリンダ部２１の内
周面に付勢して密接させ、ばね３１によりシール部材３
３をガイド部２３とハルツリテーナ２５に付勢して密接
させることによりシールを確実に行なうものである。な
お、固定ベーン２７にもこの構造か適用される。Here, an example of a seal structure for sealing each oil chamber 29A, 29B will be shown. As shown in FIG. 3, grooves 28a and 28b are formed on both side surfaces and the tip surface of the movable vane 28, and each groove 28a
, 28b, a sealing member 32 having a concave cross section is slidably fitted to the tip side of the movable vane 28, and an L-shaped sealing member 32 is fitted into the side groove 28b. A seal member 33 is slidably fitted therein. Then, the spring 30 urges the seal member 32 against the inner circumferential surface of the cylinder portion 21 to bring it into close contact with the inner circumferential surface of the cylinder portion 21, and the spring 31 causes the seal member
3 is urged against the guide portion 23 and the Harutz retainer 25 to bring them into close contact with each other, thereby ensuring reliable sealing. Note that this structure is also applied to the fixed vane 27.
第１図と第２図に戻って、前記ハウジング２０のキャッ
プ部２４とバルブリテーナ２５の間には調整油室３４か
画成されており、調整油室３４と各油室２９Ａ、２９Ｂ
とはそれぞれハルツリテーナ２５に形成された二つの通
路３５．３６で連通されている。Returning to FIGS. 1 and 2, an adjustment oil chamber 34 is defined between the cap portion 24 of the housing 20 and the valve retainer 25, and the adjustment oil chamber 34 and each oil chamber 29A, 29B.
are communicated with each other by two passages 35 and 36 formed in the Harz retainer 25, respectively.
一方の通路３５の調整油室３４偏に開口する部分には、
環状の溝３７か形成されており、この環状の溝３７を塞
ぐように減衰力発生機構であるディスクハルプ３８か配
置されている。また、他方の通路３６には、調整油室３
４内から油室２９Ａ、２９Ｂ内への油液流動は許容する
か、逆に油室２９Ａ、２９Ｂ内から調整油室３４内への
油液の流動は規制する逆止弁３９か配置されている。In the part of one passage 35 that opens toward the adjustment oil chamber 34,
An annular groove 37 is formed, and a disc harp 38, which is a damping force generating mechanism, is arranged so as to close this annular groove 37. Further, the other passage 36 includes an adjustment oil chamber 3.
A check valve 39 is arranged to allow the flow of oil from inside the oil chambers 4 to the oil chambers 29A, 29B, or to restrict the flow of oil from the inside of the oil chambers 29A, 29B to the adjustment oil chamber 34. There is.
回転軸２２には穴４０か他端側端面から軸方向に形成さ
れており、穴４０の内部にはフリーピストン４１か摺動
自在に配置されている。そして、フリーピストン４１に
より区画される室には高圧のカスか封入され高圧ガス室
４２か構成されている。また、穴４０の開口側は調整油
室３４と連通している。A hole 40 is formed in the rotating shaft 22 in the axial direction from the other end side, and a free piston 41 is slidably disposed inside the hole 40. The chamber defined by the free piston 41 is filled with high-pressure gas to form a high-pressure gas chamber 42. Further, the opening side of the hole 40 communicates with the adjustment oil chamber 34.
このフリーピストン４１と高圧ガス室４２との構成によ
れば、外気の温度によって油液か膨張または収縮したり
、油液か微少に漏れたりして油液の体積か増減した場合
に、フリーピストン４１か穴４０内を摺動して油液の体
積の補償をするため、油液が膨張したときの異常な圧力
上昇により各部材を損傷させることがなく、また、油液
か収縮したり漏れたときに油室２９Ａ、２９Ｂや調整油
室３４内に真空部か生しるのを防止することかできる。According to this configuration of the free piston 41 and the high pressure gas chamber 42, when the oil liquid expands or contracts depending on the temperature of the outside air, or when the oil liquid slightly leaks and the volume of the oil liquid increases or decreases, the free piston 41 and holes 40 to compensate for the volume of the oil, it prevents damage to each member due to abnormal pressure rise when the oil expands, and prevents the oil from contracting or leaking. It is possible to prevent a vacuum from forming in the oil chambers 29A, 29B and the adjustment oil chamber 34 when the oil chambers 29A, 29B and the regulating oil chamber 34 occur.
以上の構成のロータリータンパ−の作動を説明する。The operation of the rotary tamper with the above configuration will be explained.
ハウジング２０に対して回転軸２２か例えば第２図の矢
印方向（時計回り方向）に回転した場合には、一方の油
室２９Ａは容積か小さくなり、他方の油室２９Ｂは容積
か大きくなる。この際、容積か小さくなる油室２９Ａか
らは、一方の通路３５を通って調整油室３４に油液か流
入し、その際にディスクバルブ３８を押し開いて減衰力
を発生する。また、容積か大きくなる油室２９Ｂには、
調整油室３４から油液か他方の通路３６に設けられてい
る逆止弁３９を通って流入する。このようにして、油液
か容積か小さくなる油室２９Ａから容積か大きくなる油
室２９Ｂへ流れるときに減衰力か発生される。なお、回
転軸２２の逆方向の回転時にも同様な作用となる。When the rotating shaft 22 rotates relative to the housing 20, for example, in the direction of the arrow in FIG. 2 (clockwise), the volume of one oil chamber 29A becomes smaller, and the volume of the other oil chamber 29B becomes larger. At this time, oil flows from the oil chamber 29A, whose volume is reduced, into the adjustment oil chamber 34 through one passage 35, and at this time, the disc valve 38 is pushed open to generate a damping force. In addition, in the oil chamber 29B whose volume increases,
Oil flows from the regulating oil chamber 34 through a check valve 39 provided in the other passage 36. In this way, a damping force is generated when the oil flows from the oil chamber 29A, which has a smaller volume, to the oil chamber 29B, which has a larger volume. Note that the same effect occurs when the rotating shaft 22 is rotated in the opposite direction.
そして、このようにロータリーダンパーを構成すると、
回転軸２２内に油室および減衰力を発生するディスクバ
ルブを設けることかなくなり回転軸２２を細くすること
ができる。そのため、ロータリーダンパーの小型化が図
れるとともに、油室２９Ａ、２９Ｂの容積を大きくとる
ことかできるため、大きな減衰力を発生させることも可
能となる。また、ディスクバルブ３８の外径寸法も制約
を受けることかなく減衰力特性の設定の自由度を高める
ことができる。このため、ロータリーダンパーの用途か
広がる。And if you configure the rotary damper like this,
Since there is no need to provide an oil chamber and a disc valve for generating damping force inside the rotating shaft 22, the rotating shaft 22 can be made thinner. Therefore, the rotary damper can be made smaller, and the volumes of the oil chambers 29A and 29B can be increased, so that it is also possible to generate a large damping force. Further, the outer diameter of the disc valve 38 is not restricted, and the degree of freedom in setting the damping force characteristics can be increased. For this reason, the applications of rotary dampers are expanding.
ところて、調整油室３４をハウジング２ｏにおける回転
軸２２の軸方向の端部に形成すると、ロータリータンパ
か軸方向に長くなるか、第５図に示すように従来軸方向
に設けられていた、油液の体積補償をするフリーピスト
ン１８と高圧ガス室Ｉ９とを回転軸２２内に設けること
によって、軸方向の長さか長くなるのを抑えることかで
きる。However, if the adjusting oil chamber 34 is formed at the axial end of the rotating shaft 22 in the housing 2o, the rotary tamper will become longer in the axial direction, or as shown in FIG. By providing the free piston 18 for compensating the volume of the oil and the high pressure gas chamber I9 within the rotating shaft 22, it is possible to suppress the length in the axial direction from increasing.
なお、上記実施例では、油液の体積補償をするために、
フリーピストン４Ｉを用いたか、第４図に示すように、
回転軸２２に穴４３を形成し、この穴４３内に、内部に
高圧ガスを封入したゴムまたは合成樹脂等の伸び縮み自
在な材料からなる袋状の体積補償部材４４を嵌め込んて
ブツシュ４５により固定するようにしだものてあっても
よい。なお、このような体積補償部材を用いると、フリ
ーピストン４１を用いた場合よりも、部品点数か少なく
、穴４３の加工精度も必要ないためコストか安くなり、
かつ、予めガスを封入したものを穴４３内に挿入するた
けであるため組付性もよいという利点かある。In addition, in the above embodiment, in order to compensate for the volume of the oil liquid,
Using the free piston 4I, as shown in Figure 4,
A hole 43 is formed in the rotating shaft 22, and a bag-shaped volume compensating member 44 made of a stretchable material such as rubber or synthetic resin filled with high-pressure gas is fitted into the hole 43, and the bushing 45 is inserted into the hole 43. There may also be a handle to secure it. In addition, when such a volume compensation member is used, the number of parts is smaller than when the free piston 41 is used, and the machining accuracy of the hole 43 is not required, so the cost is lower.
In addition, since it is only necessary to insert the gas filled in advance into the hole 43, it has the advantage of being easy to assemble.
なお、上記各実施例においては、固定ベーン２７と可動
ベーン２８とをそれぞれ４枚設けて８つの油室２９Ａ、
２９Ｂを画成したか、固定ベーン２７と可動ベーン２８
とはそれぞれ１〜３枚（２〜６油室）または５枚（１０
油室）以上であってもよい。In each of the above embodiments, four fixed vanes 27 and four movable vanes 28 are provided to provide eight oil chambers 29A,
29B, a fixed vane 27 and a movable vane 28
and 1 to 3 sheets (2 to 6 oil chambers) or 5 sheets (10 oil chambers) respectively.
oil chamber) or more.
また、通路３５．３６を固定ベーン２７に近づけて設け
る程可動ベーン２８の回動範囲を大きくすることかてき
る。Further, the closer the passages 35, 36 are provided to the fixed vane 27, the larger the range of rotation of the movable vane 28 can be.
さらに、上記各実施例では回転軸２２の回転の両方向に
おいて減衰力を発生させるものとして述べたか、回転軸
２２の一方向の回転時のみ減衰力を発生させればよい場
合には次のように構成してもよい。すなわち、例えば、
第２図の矢印方向（時計回り方向）に回転した場合にの
み減衰力を発生させる場合、油室２９Ａの通路３６及び
逆止弁３９並びに油室２９Ｂの通路３５を省略し、固定
ベーン２７または可動ベーン２８のいずれかに油室２９
Ｂから油室２９Ａへのみ油液の流通を許す逆止弁を設け
る構成としてもよい。Furthermore, in each of the above embodiments, the damping force is generated in both directions of the rotation of the rotating shaft 22, but if it is necessary to generate the damping force only when the rotating shaft 22 rotates in one direction, the following method may be used. may be configured. That is, for example,
When the damping force is generated only when rotating in the direction of the arrow (clockwise) in FIG. An oil chamber 29 in either of the movable vanes 28
It is also possible to provide a check valve that allows the oil to flow only from B to the oil chamber 29A.
（発明の効果）
以１−詳細に説明したように本発明は、ハウジングと回
転軸との間に、固定ベーンと可動ベーンとて複数の油室
を画成し、ハウジングにおける回転軸の軸方向の端部に
調整油室を形成し、調整油室と各油室とを、油室から調
整油室への油液の流動により減衰力を発生する減衰力発
生機構を設けた通路と、調整油室から油室への油液の波
動のみを許容する逆止弁を設けた通路でそれぞれ連通さ
せる構成としたため、回転軸内に油室および減衰力発生
機構を設けることかなくなり回転軸を細くすることかて
き、ロータリーダンパーの小型化を図ることかてきる。(Effects of the Invention) 1. As described in detail, the present invention includes a fixed vane and a movable vane that define a plurality of oil chambers between the housing and the rotating shaft, and the axial direction of the rotating shaft in the housing. An adjustment oil chamber is formed at the end of the adjustment oil chamber, and the adjustment oil chamber and each oil chamber are connected to a passage provided with a damping force generation mechanism that generates a damping force by the flow of oil from the oil chamber to the adjustment oil chamber. Since the oil chamber is configured to communicate with each other through passages equipped with check valves that allow only the wave motion of oil fluid from one oil chamber to another, there is no need to provide an oil chamber or a damping force generation mechanism within the rotating shaft, allowing the rotating shaft to be thinner. One thing to do is to make the rotary damper more compact.
また、従来のロータリータンパ−と同一の外径てあって
も油室の容積を大きくとることかでき、作動流量を多く
することかてきて大きな減衰力を発生させることも可能
となり、かつ、減衰力発生機構の外径寸法も自由に設定
することかてきるため、減衰力特性の設定の自由度を高
めることかてきる。これにより、自動二輪の緩衝機構か
ら大きな減衰力を必要とする自動車のスタビライザの緩
衝機構に至るまで幅広い用途に適用することかてきる。In addition, even if the outer diameter is the same as that of a conventional rotary tamper, the volume of the oil chamber can be increased, and by increasing the operating flow rate, it is possible to generate a large damping force. Since the outer diameter of the force generating mechanism can also be freely set, the degree of freedom in setting the damping force characteristics can be increased. This allows it to be applied to a wide range of applications, from motorcycle shock absorbing mechanisms to automobile stabilizer shock absorbing mechanisms that require large damping forces.
さらに、減衰力発生機構をハウジングの端部に設けたた
め組付性か良好となり、生産性の向上か図れる。Furthermore, since the damping force generating mechanism is provided at the end of the housing, ease of assembly is improved, and productivity can be improved.
第１図は、本発明の一実施例の断面を有する側面図、
第２図は、第１図のＩＩ−ＩＩ線断面図、第３図は、ヘ
ーンのシール構造の一例を示す分解斜視図、
第４図は、ハウジング内に封入されている油液の体積補
償をする構造の他の例を示す要部断面図、
第５図は、従来のロータリーダンパーの一部断面を有す
る側面図、
第６図は、第４図のＶＩ−ＶＩ線断面図である。
２０・・・ハウシング ２２・・・回転軸２７・・
・固定ベーン ２８・・・可動ベーン２９Ａ、２９
Ｂ・・・油室 ３４・・・調整油室３５．３６・・
・通路
３８・・・ディスクハルツ（減衰力発生機構）３９・・
・逆止弁
第１図FIG. 1 is a cross-sectional side view of an embodiment of the present invention, FIG. 2 is a sectional view taken along line II-II in FIG. 1, and FIG. 3 is an exploded perspective view showing an example of the Hoene seal structure. , FIG. 4 is a sectional view of a main part showing another example of a structure for volume compensation of oil sealed in a housing, FIG. 5 is a side view with a partial cross section of a conventional rotary damper, FIG. 6 is a sectional view taken along the line VI-VI in FIG. 4. 20...Housing 22...Rotating shaft 27...
・Fixed vane 28...Movable vane 29A, 29
B...Oil chamber 34...Adjustment oil chamber 35.36...
・Passage 38... Disk Harz (damping force generation mechanism) 39...
・Check valve diagram 1
Claims (2)
転可能に設けた回転軸との間に、ハウジングに取付けた
一以上の固定ベーンと回転軸に取付けた一以上の可動ベ
ーンとを該回転軸の周回り方向に配置して複数の油室を
画成し、ハウジングにおける回転軸の軸方向の端部に調
整油室を形成し、該調整油室と前記各油室とを通路で連
通させ、該通路に、油室から調整油室への油液の流動に
より減衰力を発生する減衰力発生機構を設け、ハウジン
グと回転軸との間の相対回転時に、容積の小さくなる油
室から減衰力発生機構及び調整油室を介して容積の大き
くなる油室へ油液が流動するように前記通路を構成して
なることを特徴とするロータリーダンパー。(1) One or more fixed vanes attached to the housing and one or more movable vanes attached to the rotating shaft are connected between a housing filled with oil and a rotating shaft rotatably provided on the housing. A plurality of oil chambers are arranged in the circumferential direction of the shaft to define a plurality of oil chambers, an adjustment oil chamber is formed at an end in the axial direction of the rotating shaft in the housing, and the adjustment oil chamber and each of the oil chambers are communicated through a passage. The passage is provided with a damping force generation mechanism that generates a damping force by the flow of oil from the oil chamber to the adjustment oil chamber, and the damping force generation mechanism is installed in the passage to generate damping force by the flow of oil from the oil chamber to the adjustment oil chamber. A rotary damper characterized in that the passage is configured so that the oil fluid flows through the damping force generation mechanism and the adjustment oil chamber to the oil chamber whose volume increases.
転可能に設けた回転軸との間に、ハウジングに取付けた
一以上の固定ベーンと回転軸に取付けた一以上の可動ベ
ーンとを該回転軸の周回り方向に配置して複数の油室を
画成し、ハウジングにおける回転軸の軸方向の端部に調
整油室を形成し、該調整油室と前記各油室とを二つずつ
の通路で連通させ、一方の通路に、油室から調整油室へ
の油液の流動により減衰力を発生する減衰力発生機構を
設 け、他方の通路に、調整油室から油室への油液の流動の
みを許容する逆止弁を設けてなることを特徴とするロー
タリーダンパー。(2) One or more fixed vanes attached to the housing and one or more movable vanes attached to the rotating shaft are connected between a housing filled with oil and a rotating shaft rotatably provided on the housing. A plurality of oil chambers are arranged in the circumferential direction of the shaft to define a plurality of oil chambers, an adjustment oil chamber is formed at an end in the axial direction of the rotating shaft in the housing, and two of the adjustment oil chambers and two of each of the oil chambers are provided. One passage is provided with a damping force generation mechanism that generates damping force by the flow of oil from the oil chamber to the adjustment oil chamber, and the other passage is equipped with a damping force generation mechanism that generates damping force by the flow of oil from the adjustment oil chamber to the oil chamber. A rotary damper characterized by being equipped with a check valve that only allows liquid to flow.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1120890A JP2916691B2 (en) | 1990-01-20 | 1990-01-20 | Rotary damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1120890A JP2916691B2 (en) | 1990-01-20 | 1990-01-20 | Rotary damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03219131A true JPH03219131A (en) | 1991-09-26 |
| JP2916691B2 JP2916691B2 (en) | 1999-07-05 |
Family
ID=11771589
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1120890A Expired - Lifetime JP2916691B2 (en) | 1990-01-20 | 1990-01-20 | Rotary damper |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2916691B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2003046405A1 (en) * | 2001-11-27 | 2003-06-05 | Kabushiki Kaisha Somic Ishikawa | Rotary damper and automobile part comprising it and auxiliary mechanism of rotary operation |
| JP2010060032A (en) * | 2008-09-03 | 2010-03-18 | Somic Ishikawa Inc | Rotary damper |
| JP2012225402A (en) * | 2011-04-18 | 2012-11-15 | Oiles Corp | Rotary damper |
-
1990
- 1990-01-20 JP JP1120890A patent/JP2916691B2/en not_active Expired - Lifetime
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2003046405A1 (en) * | 2001-11-27 | 2003-06-05 | Kabushiki Kaisha Somic Ishikawa | Rotary damper and automobile part comprising it and auxiliary mechanism of rotary operation |
| US7066308B2 (en) | 2001-11-27 | 2006-06-27 | Kabushiki Kaisha Somic Ishikawa | Rotary damper and automobile part comprising it and auxiliary mechanism of rotary operation |
| US7204353B2 (en) | 2001-11-27 | 2007-04-17 | Kabushiki Kaisha Somic Ishikawa | Rotary damper, auto part having rotary damper and rotational motion assistant mechanism |
| JP2010060032A (en) * | 2008-09-03 | 2010-03-18 | Somic Ishikawa Inc | Rotary damper |
| JP2012225402A (en) * | 2011-04-18 | 2012-11-15 | Oiles Corp | Rotary damper |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2916691B2 (en) | 1999-07-05 |
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