JPS6215780B2 - - Google Patents
Info
- Publication number
- JPS6215780B2 JPS6215780B2 JP54057713A JP5771379A JPS6215780B2 JP S6215780 B2 JPS6215780 B2 JP S6215780B2 JP 54057713 A JP54057713 A JP 54057713A JP 5771379 A JP5771379 A JP 5771379A JP S6215780 B2 JPS6215780 B2 JP S6215780B2
- Authority
- JP
- Japan
- Prior art keywords
- wall element
- annular wall
- rubber
- annular
- stopper
- 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
- 238000005192 partition Methods 0.000 claims description 8
- 238000010008 shearing Methods 0.000 claims description 7
- 230000001747 exhibiting effect Effects 0.000 claims description 2
- 238000013016 damping Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 230000005489 elastic deformation Effects 0.000 description 4
- 239000012530 fluid Substances 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000004073 vulcanization Methods 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
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Combined Devices Of Dampers And Springs (AREA)
Description
【発明の詳細な説明】
本発明は、防振ゴム装置に係り、特に自動車等
の車輛に於いてエンジンを車体に装着するために
用いられるエンジンマウンテイング用防振ゴム装
置に係る。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vibration isolating rubber device, and more particularly to a vibration isolating rubber device for engine mounting used to mount an engine to a vehicle body of a vehicle such as an automobile.
エンジンマウンテイング用防振ゴム装置は、従
来一般に、ゴム等のゴム状弾性体を含んでおり、
これによつてエンジンを弾性的に支持し、エンジ
ンと車体との間にある程度の相対的変位を許し、
これによつてエンジンの振動が車体に伝わること
を前記ゴム状弾性体の弾性変形によつて防止せん
とするものである。 Conventionally, anti-vibration rubber devices for engine mounting generally include a rubber-like elastic body such as rubber.
This elastically supports the engine and allows a certain degree of relative displacement between the engine and the vehicle body.
This is intended to prevent engine vibrations from being transmitted to the vehicle body through elastic deformation of the rubber-like elastic body.
ところで、自動車等に於いて、高周波、小振幅
のエンジン振動が車体に伝わらないようにするた
めには、防振ゴム装置は比較的小さいばね定数を
有していることが好ましい。しかしこの反面、悪
路走行時等の生じる低周波、大振幅の振動に対し
ては、防振ゴム装置は比較的大きいばね定数を有
していることが好ましい。また、低周波、中振幅
の振動に対しても振動の減衰を行なうべく防振ゴ
ムは振動減衰能を有していることが好ましい。 By the way, in order to prevent high-frequency, small-amplitude engine vibrations from being transmitted to the vehicle body in automobiles and the like, it is preferable that the vibration-isolating rubber device has a relatively small spring constant. However, on the other hand, it is preferable that the anti-vibration rubber device has a relatively large spring constant to withstand low-frequency, large-amplitude vibrations that occur when driving on rough roads. Further, it is preferable that the vibration isolating rubber has a vibration damping ability so as to damp vibrations even in low frequency and medium amplitude vibrations.
本発明は、高周波、小振幅の振動に対しては比
較的小さいばね定数の特性を呈し、低周波、大振
幅の振動に対しては大きいばね定数のばね特性を
呈し、しかも優れた振動減衰能を有し、幅広い周
波数領域にて充分な防振効果を発揮し、更にゴム
状弾性体が過剰変形することを防止するストツパ
構造を備えた新しい防振ゴム装置を提供すること
を目的としている。 The present invention exhibits characteristics of a relatively small spring constant for high-frequency, small-amplitude vibrations, and exhibits characteristics of a large spring constant for low-frequency, large-amplitude vibrations, and has excellent vibration damping performance. It is an object of the present invention to provide a new vibration-isolating rubber device that exhibits a sufficient vibration-isolating effect in a wide frequency range and is further equipped with a stopper structure that prevents excessive deformation of a rubber-like elastic body.
かかる目的は、本発明によれば、互に向かい合
つた壁面を呈する二つの枠体と、前記両枠体の前
記壁面間に延在し該壁面と共働して該壁面間に一
つの室空間を郭定する円環状断面のゴム状弾性体
の環状壁要素と、前記二つの枠体のうちのいずれ
か一方に固定され前記室空間に対する空気の出入
を行う絞り通路を有する仕切部材と、前記環状壁
要素が前記枠体間にて所定量以上圧縮された時に
は前記環状壁要素がそれ以上圧縮変形することを
抑制し且つ前記絞り通路を塞ぐゴム状弾性体のス
トツパ要素とを有し、前記仕切部材は半球状をな
していて前記室空間内に突出して前記環状壁要素
の内周面に所定間隔をおいて対向し前記環状壁要
素の剪断方向のストツパを兼ねていることを特徴
とする防振ゴム装置によつて達成される。 According to the present invention, the present invention provides two frames having mutually facing wall surfaces, and a chamber extending between and cooperating with the wall surfaces of both the frame bodies. an annular wall element made of a rubber-like elastic body with an annular cross section that defines a space; a partition member that is fixed to either one of the two frames and has a throttle passage that allows air to enter and exit the room space; a stopper element made of a rubber-like elastic body that suppresses further compressive deformation of the annular wall element and closes the throttle passage when the annular wall element is compressed by a predetermined amount or more between the frames; The partition member has a hemispherical shape, projects into the room space, faces the inner peripheral surface of the annular wall element at a predetermined interval, and also serves as a stopper in the shearing direction of the annular wall element. This is achieved by a vibration isolating rubber device.
上述の如き構成によれば、前記環状壁要素は比
較的小さいばね定数を有するゴム状弾性体で構成
されてよく、これにより高周波、小振幅の振動の
伝達を効果的に抑制し、騒音の発生を防止するこ
とができる。また、前記環状壁要素の変形に伴い
室空間内の空気の出入が仕切部材の絞り通路を経
て行なわれるので、その際の流体粘性抵抗により
振動の減衰効果が得られ、特に低周波、中振幅の
振動の減衰が行われるようになる。また、環状壁
要素は所定量圧縮されると、ストツパ要素により
それ以上圧縮変形することを抑制され、また前記
絞り通路が前記ストツパ要素によつて閉じられ、
室空間が空気ばねを構成することにより防振ゴム
装置全体の実質的なばね定数が増大するようにな
る。従つて環状壁要素を所定量以上圧縮変形させ
る如き低周波、水振幅の振動はこの時には比較的
高いばね定数のばね特性を呈する防振ゴム装置に
よつて効果的に減衰される。また環状壁要素が所
定量以上剪断方向に弾性変形した時には環状壁要
素が仕切部材に当接し、これにより環状壁要素が
過剰に剪断方向に弾性変形することが抑制され、
併せて環状壁要素の耐久性が確保されるようにな
る。この環状壁要素の剪断方向のストツパは内部
の仕切部材により構成されているから、部品点数
の削減と防振ゴム装置全体のコンパクト化が図ら
れるようになる。 According to the above configuration, the annular wall element may be made of a rubber-like elastic body having a relatively small spring constant, thereby effectively suppressing the transmission of high-frequency, small-amplitude vibrations and reducing the generation of noise. can be prevented. In addition, as the annular wall element deforms, air enters and exits the room space through the constriction passage of the partition member, so the fluid viscous resistance at that time provides a vibration damping effect, especially at low frequencies and medium amplitudes. vibrations are now damped. Further, when the annular wall element is compressed by a predetermined amount, the stopper element prevents the annular wall element from being further compressed and deformed, and the throttle passage is closed by the stopper element,
Since the room space constitutes an air spring, the substantial spring constant of the entire vibration isolating rubber device increases. Therefore, low-frequency, water-amplitude vibrations that cause compressive deformation of the annular wall element by more than a predetermined amount are effectively damped by the vibration-isolating rubber device exhibiting spring characteristics with a relatively high spring constant. Further, when the annular wall element is elastically deformed in the shearing direction by a predetermined amount or more, the annular wall element comes into contact with the partition member, thereby suppressing excessive elastic deformation of the annular wall element in the shearing direction.
At the same time, the durability of the annular wall element is ensured. Since the stopper in the shearing direction of the annular wall element is constituted by an internal partition member, the number of parts can be reduced and the entire vibration isolating rubber device can be made more compact.
上述の如き防振ゴム装置がエンジンマウンテイ
ング用防振ゴム装置として用いられれば、吸振作
用とストツパ作用により優れた耐久性の下に騒音
の低減と乗心地の向上が両立するようになる。 If the vibration isolating rubber device as described above is used as a vibration isolating rubber device for engine mounting, it will be possible to reduce noise and improve riding comfort while having excellent durability due to its vibration absorbing and stopper effects.
以下に添付の図を用いて本発明を実施例につい
て詳細に説明する。 DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described in detail below with reference to the accompanying drawings.
添付の図は本発明による防振ゴム装置の一つの
実施例を示す縦断面図である。図に於いて、１及
び２は枠体を示しており、この枠体１，２は互に
向かい合つた壁面３，４を有するように構成され
ている。枠体１はこれをエンジン、或は車体に固
定するための取付ボルト５が取付けられている。
枠体２は、円環状をなし、締結ボルト６、ワツシ
ヤ７、締結ナツト８によつてカバープレート９に
連結されており、このカバープレート９にはこれ
をエンジン、或は車体に固定するための取付ボル
ト１０が取付けられている。前記枠体２と１との
間にはそれらの壁面３及び４の間に延在してゴム
状弾性体からなる円錘形状、即ち円環状断面の環
状壁要素１１が加硫接着により設けられている。
この環状壁要素１１の外周の一部には該環状壁要
素の拡径変形を抑制する円環状の外輪プレート１
１′が取付けられている。前記枠体２と前記カバ
ープレート９とは互に共働して金属で構成された
仕切部材としての半球状壁要素１２及びゴム或は
ゴム類似品によつて構成されたダイヤフラム１３
を担持している。前記半球状壁要素１２は前記枠
体２より前記環状壁要素１１の内側に突出し該環
状壁要素１１と共働して第一の室空間１４を郭定
している。換言すれば、半球状壁要素１１は、第
一の室空間１４内に突出し、環状壁要素１１の内
周面に所定間隔をおいて対向している。また前記
半球状壁要素１２は前記第一の室空間１４の反対
側に前記ダイヤフラム１３と共働して第二の室空
間１５を郭定している。前記第一の室空間１４と
前記第二の室空間１５とは前記半球状壁要素１２
の中央頂部に設けられた絞り孔１６を経て互に連
通接続されている。また前記ダイヤフラム１３は
前記カバープレート９との間にもう一つの室空間
１７を郭定しており、この室空間１７は大気開放
孔１８を経て大気中に開放されている。また前記
枠体１の壁面３には前記環状壁要素１１と一体に
ゴム状弾性体によつて構成されたストツパ要素１
９が突出形成されている。このストツパ要素１９
は、図にて仮想線で示されている如く、前記環状
壁要素１１が所定量圧縮変形すると、前記半球状
壁要素１２に当接し、且つ前記絞り孔１６を塞ぐ
ようになつている。 The attached figure is a longitudinal cross-sectional view showing one embodiment of the vibration isolating rubber device according to the present invention. In the figure, 1 and 2 indicate frames, and the frames 1 and 2 are constructed to have wall surfaces 3 and 4 facing each other. Mounting bolts 5 are attached to the frame 1 for fixing it to an engine or a vehicle body.
The frame body 2 has an annular shape and is connected to a cover plate 9 by a fastening bolt 6, a washer 7, and a fastening nut 8. Mounting bolts 10 are attached. Between the frames 2 and 1, an annular wall element 11 made of a rubber-like elastic body and having a conical shape, that is, an annular cross section, is provided by vulcanization adhesion and extends between the wall surfaces 3 and 4. ing.
A part of the outer periphery of this annular wall element 11 is provided with an annular outer ring plate 1 for suppressing radially expanding deformation of the annular wall element.
1' is attached. The frame body 2 and the cover plate 9 cooperate with each other and include a hemispherical wall element 12 as a partition member made of metal and a diaphragm 13 made of rubber or rubber-like material.
is carried. The hemispherical wall element 12 projects inside the annular wall element 11 from the frame 2 and cooperates with the annular wall element 11 to define a first chamber space 14 . In other words, the hemispherical wall element 11 protrudes into the first chamber space 14 and faces the inner peripheral surface of the annular wall element 11 at a predetermined distance. The hemispherical wall element 12 also cooperates with the diaphragm 13 to define a second chamber space 15 on the opposite side of the first chamber space 14 . The first chamber space 14 and the second chamber space 15 are defined by the hemispherical wall element 12.
are connected to each other through a throttle hole 16 provided at the center top of the tubes. Further, the diaphragm 13 defines another chamber space 17 between it and the cover plate 9, and this chamber space 17 is opened to the atmosphere through an atmosphere opening hole 18. Further, on the wall surface 3 of the frame 1, a stopper element 1 is integrally formed with the annular wall element 11 and is made of a rubber-like elastic body.
9 is formed protrudingly. This stopper element 19
As shown by imaginary lines in the figure, when the annular wall element 11 is compressed and deformed by a predetermined amount, it comes into contact with the hemispherical wall element 12 and closes the throttle hole 16.
以上の如く構成されていることにより、枠体１
と２との間に振動荷重が与えられると、環状壁要
素１１は弾性変形により伸縮し、枠体１と２との
間に振動が、特に、高周波、小振幅の振動が伝わ
ることを抑制する。また、環状壁要素１１が伸縮
することにより第一の室空間１４内の流体、この
実施例の場合、空気が絞り孔１６を経て第二の室
空間１５に対し出入し、その際の流体粘性抵抗に
より振動の減衰効果が得られる。この場合、第二
の室空間１５がダイヤフラム１３によつて大気中
より遮断されているので、絞り孔１６を空気が通
過する際に生じる流動音が大気中に放射されるこ
とが防止される。前記環状壁要素１１が大きく圧
縮変形し、それが所定値以上になると、図にて仮
想線で示されている如く、ストツパ要素１９が半
球状壁要素１４の中央頂部に当接し、また前記絞
り孔１６を閉じるようになる。従つて、環状壁要
素１１が所定量以上圧縮された時には環状壁要素
１１自体のばね荷重に加えてストツパ要素１９の
ばね荷重及び第一の室空間１４が密閉されること
によつて構成される空気ばねのばね荷重が作用
し、防振ゴム装置全体のばね定数が大きくなる。
これにより悪路走行時等によつて生じる低周波、
大振幅の振動が防振ゴム装置に与えられてもこれ
が増幅されるようなことがない。 With the above configuration, the frame 1
When a vibration load is applied between the frames 1 and 2, the annular wall element 11 expands and contracts due to elastic deformation, suppressing the transmission of vibrations, especially high-frequency, small-amplitude vibrations, between the frames 1 and 2. . Furthermore, as the annular wall element 11 expands and contracts, the fluid in the first chamber space 14, in the case of this embodiment, air, enters and exits the second chamber space 15 through the throttle hole 16, and the fluid viscosity at that time increases. The resistance provides a vibration damping effect. In this case, since the second chamber space 15 is isolated from the atmosphere by the diaphragm 13, flow noise generated when air passes through the throttle hole 16 is prevented from being radiated into the atmosphere. When the annular wall element 11 is greatly compressed and deformed to a predetermined value or more, the stopper element 19 comes into contact with the central top of the hemispherical wall element 14, as shown by the imaginary line in the figure, and the aperture The hole 16 is now closed. Therefore, when the annular wall element 11 is compressed by a predetermined amount or more, in addition to the spring load of the annular wall element 11 itself, the spring load of the stopper element 19 and the first chamber space 14 are sealed. The spring load of the air spring acts, increasing the spring constant of the entire vibration isolating rubber device.
As a result, low frequencies generated when driving on rough roads, etc.
Even if large amplitude vibrations are applied to the vibration isolating rubber device, the vibrations will not be amplified.
絞り孔１６を塞がなくてもストツパ要素１９が
設けられていると、環状壁要素１１が所定量以上
圧縮されれば、環状壁要素１１がそれ以上圧縮さ
れることに関し前記ストツパ要素１９が新たに抗
力を発生するから防振ゴム装置は全体として非線
型のばね特性を有するようになるが、ストツパ要
素１９による抗力だけではばね定数の微調整が難
しく、所望するばね特性を示す防振ゴム装置を得
ることが難しい。これに対して絞り通路１６を塞
いで第一の室空間１４を空気ばねとして作用させ
れば、ばね定数の微調整を比較的容易に行なえ、
また実際にはストツパ要素１９が徐々に絞り通路
１６を塞ぐようになるため、ストツパ要素１９が
半球状壁要素１２に当接した時点で防振ゴム装置
全体のばね係数が急激に増大することがなく、
徐々に増大するようになり、所望するばね特性を
有する防振ゴム装置を具現することができる。 If the stopper element 19 is provided even if the throttle hole 16 is not blocked, if the annular wall element 11 is compressed by a predetermined amount or more, the stopper element 19 will prevent the annular wall element 11 from being compressed further. The anti-vibration rubber device as a whole has non-linear spring characteristics due to the generation of drag force, but it is difficult to finely adjust the spring constant with only the drag force generated by the stopper element 19, and the vibration-isolating rubber device has non-linear spring characteristics. difficult to obtain. On the other hand, if the throttle passage 16 is closed and the first chamber space 14 acts as an air spring, the spring constant can be finely adjusted relatively easily.
Furthermore, in reality, the stopper element 19 gradually closes the throttle passage 16, so that the spring coefficient of the entire vibration-isolating rubber device increases rapidly when the stopper element 19 comes into contact with the hemispherical wall element 12. Without,
It is possible to realize a vibration isolating rubber device having the desired spring characteristics by gradually increasing the spring characteristics.
環状壁要素１１が剪断方向、即ち図にて左右方
向に大きく弾性変形すると、その内周面が半球状
壁要素１２の外周面に当接するようになり、それ
以上環状壁要素１１が剪断方向に弾性変形するこ
とが抑制される。 When the annular wall element 11 is largely elastically deformed in the shearing direction, that is, in the horizontal direction in the figure, its inner circumferential surface comes into contact with the outer circumferential surface of the hemispherical wall element 12, and the annular wall element 11 no longer moves in the shearing direction. Elastic deformation is suppressed.
以上に於いては本発明を特定の実施例について
詳細に説明したが、本発明はこれに限られるもの
ではなく、本発明の範囲内にて種々の実施例が可
能であることは当業者にとつて明らかであろう。 Although the present invention has been described in detail with respect to specific embodiments above, it will be understood by those skilled in the art that the present invention is not limited thereto, and that various embodiments are possible within the scope of the present invention. It should be obvious.
添付の図は本発明による防振ゴム装置の一つの
実施例を示す縦断面図である。
１，２〜枠体、３，４〜壁面、５〜取付ボル
ト、６〜締結ボルト、７〜ワツシヤ、８〜締結ナ
ツト、９〜カバープレート、１０〜取付ボルト、
１１〜環状壁要素、１２〜半球状壁要素、１３〜
ダイヤフラム、１４〜第一の室空間、１５〜第二
の室空間、１６〜絞り孔、１７〜室空間、１８〜
大気開放孔、１９〜ストツパ要素。
The attached figure is a longitudinal cross-sectional view showing one embodiment of the vibration isolating rubber device according to the present invention. 1, 2 - frame body, 3, 4 - wall surface, 5 - mounting bolt, 6 - fastening bolt, 7 - washer, 8 - fastening nut, 9 - cover plate, 10 - mounting bolt,
11~Annular wall element, 12~Semispherical wall element, 13~
Diaphragm, 14-first chamber space, 15-second chamber space, 16-diaphragm hole, 17-chamber space, 18-
Atmospheric opening hole, 19~stopper element.
Claims (1)
と、前記両枠体の前記壁面間に延在し該壁面と共
働して該壁面間に一つの室空間を郭定する円環状
断面のゴム状弾性体の環状壁要素と、前記二つの
枠体のうちのいずれか一方に固定され前記室空間
に対する空気の出入を行う絞り通路を有する仕切
部材と、前記環状壁要素が前記枠体間にて所定量
以上圧縮された時には前記環状壁要素がそれ以上
圧縮変形することを抑制し且つ前記絞り通路を塞
ぐゴム状弾性体のストツパ要素とを有し、前記仕
切部材は半球状をなしていて前記室空間内に突出
して前記環状壁要素の内周面に所定間隔をおいて
対向し前記環状壁要素の剪断方向のストツパを兼
ねていることを特徴とする防振ゴム装置。1. Two frames exhibiting wall surfaces facing each other, and an annular cross section extending between the wall surfaces of the two frame bodies and cooperating with the wall surfaces to define one chamber space between the wall surfaces. an annular wall element made of a rubber-like elastic body; a partition member fixed to one of the two frames and having a throttle passage for allowing air to enter and exit the room space; and an annular wall element formed between the frames. and a stopper element made of a rubber-like elastic body that suppresses further compressive deformation of the annular wall element and closes the throttle passage when the annular wall element is compressed by a predetermined amount or more, and the partition member has a hemispherical shape. A vibration isolating rubber device, characterized in that the rubber device protrudes into the room space, faces the inner circumferential surface of the annular wall element at a predetermined distance, and also serves as a stopper in the shearing direction of the annular wall element.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5771379A JPS55149436A (en) | 1979-05-10 | 1979-05-10 | Vibration resisting rubber device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5771379A JPS55149436A (en) | 1979-05-10 | 1979-05-10 | Vibration resisting rubber device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS55149436A JPS55149436A (en) | 1980-11-20 |
| JPS6215780B2 true JPS6215780B2 (en) | 1987-04-09 |
Family
ID=13063580
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP5771379A Granted JPS55149436A (en) | 1979-05-10 | 1979-05-10 | Vibration resisting rubber device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS55149436A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02118396U (en) * | 1989-03-09 | 1990-09-21 | ||
| JPH0545931U (en) * | 1991-11-19 | 1993-06-18 | 株式会社白山製作所 | Crocodile clip |
Families Citing this family (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0053401B1 (en) * | 1980-12-03 | 1986-05-28 | Nissan Motor Co., Ltd. | Fluid-filled engine mount device |
| US4483521A (en) * | 1981-07-01 | 1984-11-20 | Nissan Motor Company, Limited | Rubber and fluid type vibration damper |
| CA1194045A (en) * | 1981-09-30 | 1985-09-24 | Isao Ozawa | Elastically damping device for the suspension of an engine |
| US4573656A (en) * | 1983-07-22 | 1986-03-04 | Honda Giken Kogyo Kabushiki Kaisha | Fluid-sealed engine mounting |
| SE449780B (en) * | 1983-09-16 | 1987-05-18 | Trelleborg Ab | VIBRATION INSULATOR WITH WIRE ABSORPTION |
| DE3336204A1 (en) * | 1983-10-05 | 1985-05-02 | Metzeler Kautschuk GmbH, 8000 München | ENGINE MOUNT WITH HYDRAULIC DAMPING |
| JPS60145636U (en) * | 1984-03-07 | 1985-09-27 | 東洋ゴム工業株式会社 | Anti-vibration rubber device |
| DE3418123A1 (en) * | 1984-05-16 | 1985-11-21 | Diehl GmbH & Co, 8500 Nürnberg | ELASTIC RUBBER BEARING WITH INTEGRATED HYDRAULIC DAMPING |
| US4903951A (en) * | 1987-05-12 | 1990-02-27 | Honda Giken Kogyo Kabushiki Kaisha | Fluid-filled vibroisolating device |
| JPH01118231U (en) * | 1987-09-08 | 1989-08-10 | ||
| JPH0624593Y2 (en) * | 1988-02-04 | 1994-06-29 | 東海ゴム工業株式会社 | Fluid-filled mounting device |
| JP2598987B2 (en) * | 1988-06-06 | 1997-04-09 | 東海ゴム工業株式会社 | Fluid-filled mounting device |
| FR2650043B1 (en) * | 1989-07-18 | 1991-10-31 | Peugeot | IMPROVED HYDRAULIC DAMPING DEVICE, PARTICULARLY FOR THE SUSPENSION OF A DRIVE UNIT OF A MOTOR VEHICLE |
| JPH04272531A (en) * | 1990-10-12 | 1992-09-29 | Metzeler Gimetall Ag | Method for varying spring rigidity for mount made of elastomer and engine mount |
| DE4041837C1 (en) * | 1990-12-24 | 1992-04-30 | Boge Ag, 5208 Eitorf, De | |
| DE4216185C2 (en) * | 1992-05-15 | 1994-12-08 | Boge Gmbh | Elastic rubber bearing |
| CN104047989B (en) * | 2014-05-23 | 2016-05-18 | 大连大学 | Positive/negative-pressure vibration isolating |
-
1979
- 1979-05-10 JP JP5771379A patent/JPS55149436A/en active Granted
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02118396U (en) * | 1989-03-09 | 1990-09-21 | ||
| JPH0545931U (en) * | 1991-11-19 | 1993-06-18 | 株式会社白山製作所 | Crocodile clip |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS55149436A (en) | 1980-11-20 |
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