WO2004067992A1 - Dispositif d'isolation des vibrations hydraulique - Google Patents

Dispositif d'isolation des vibrations hydraulique Download PDF

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Publication number
WO2004067992A1
WO2004067992A1 PCT/JP2003/004584 JP0304584W WO2004067992A1 WO 2004067992 A1 WO2004067992 A1 WO 2004067992A1 JP 0304584 W JP0304584 W JP 0304584W WO 2004067992 A1 WO2004067992 A1 WO 2004067992A1
Authority
WO
WIPO (PCT)
Prior art keywords
liquid
vibration
flow path
piston
mounting member
Prior art date
Application number
PCT/JP2003/004584
Other languages
English (en)
Japanese (ja)
Inventor
Toshifumi Sakata
Mie Kanki
Kazumasa Kuze
Original Assignee
Toyo Tire & Rubber Co., Ltd.
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Toyo Tire & Rubber Co., Ltd. filed Critical Toyo Tire & Rubber Co., Ltd.
Priority to AU2003236069A priority Critical patent/AU2003236069A1/en
Publication of WO2004067992A1 publication Critical patent/WO2004067992A1/fr

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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
    • F16F13/26—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 characterised by adjusting or regulating devices responsive to exterior conditions
    • 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
    • F16F2224/00—Materials; Material properties
    • F16F2224/04—Fluids
    • F16F2224/045—Fluids magnetorheological

Definitions

  • the present invention relates to a liquid filled type vibration damping device mainly used for supporting a vibration body such as an automobile engine in a vibration damping manner.
  • a liquid-filled type vibration damping device in general, includes two mounting brackets respectively attached to a support side of a vehicle body frame or the like and a vibration generator side of an engine or the like, a vibration isolating base made of a rubber material connecting the both mounting brackets, A main liquid chamber in which a part of the chamber wall is formed by the vibration isolating base; and a sub liquid chamber in which a part of the chamber wall is formed by the diaphragm and connected to the main liquid chamber through an orifice.
  • the orifice is configured to perform a vibration damping function by the liquid flow effect between the two liquid chambers and the vibration damping effect of the vibration isolating base.
  • a liquid-filled type vibration damping device provided with a plurality of orifices so as to cope with vibrations in different frequency ranges such as shake vibration and idle vibration.
  • a main liquid chamber and a sub liquid chamber are provided in a partition section that separates the main liquid chamber and the sub liquid chamber.
  • a first orifice connecting the chambers is provided, and a second sub-liquid chamber and a second orifice communicating with the second sub-liquid chamber are provided.
  • the first orifice absorbs, for example, shake vibration
  • the second orifice for example, absorbs shake vibration. It is configured to absorb idle vibration.
  • liquid-filled vibration isolators that can absorb fluctuations in the liquid pressure in the main liquid chamber due to the effect of the liquid flowing through the orifice against vibrations in the low frequency range.
  • the state is the same as when the orifice is closed, so that fluctuations in hydraulic pressure in the main fluid chamber cannot be absorbed, and therefore vibrations in the high frequency range are good.
  • vibrations in the high frequency range are good.
  • Japanese Patent Publication No. 2002-2609691 discloses a vibration isolator as shown in FIG.
  • a cylindrical lower mounting bracket 101 and an upper mounting bracket 102 arranged on the axis thereof are connected via a vibration isolating base 103 to form a lower mounting bracket.
  • a diaphragm 104 is provided at the lower side of 101, and a liquid chamber between the vibration-proof base 103 and the upper main liquid chamber 106 and a lower auxiliary liquid chamber 1 are separated by a partition 105.
  • the two liquid chambers 106 and 107 are connected by an orifice 108 so that a supporting load is applied in the direction in which the main liquid chamber 106 is compressed.
  • the partition 105 is configured to be displaceable in a direction in which the volumes of the upper and lower liquid chambers 106 and 107 are relatively variable, and the ease of displacement of the partition 105 is adjusted.
  • a flow path 109 that holds the MR fluid whose viscosity can be increased or decreased according to the magnetic field strength, and an electromagnet 110 that can control the magnetic field strength are provided.
  • the dynamic spring constant of the partition portion 105 can be made variable so that vibration-proof performance against vibration in a wide frequency range can be exhibited.
  • the electromagnet 110 is integrated with the partition portion 105 to reduce the overall size of the device.
  • the partition portion 105 is provided with the electromagnet 110.
  • an opening is provided in the center of the diaphragm 104, the opening periphery 104A is connected to the lower surface of the partition 105, and the lead wire 111 is drawn out from the inside of the connection.
  • the lead wire 111 is connected without passing through the inside of the auxiliary liquid chamber 107.
  • the present invention has been made in view of the above points, and provides a liquid-sealed type vibration damping device that can exhibit vibration damping performance in a wide frequency range without impairing the durability of the diaphragm.
  • the purpose is to:
  • the liquid-filled type vibration damping device of the present invention includes: a first cylindrical mounting member; a second mounting member disposed inside the first mounting member; and a second mounting member interposed between the mounting members.
  • a suspension type vibration isolating base comprising a rubber material for joining members, wherein a supporting load is applied in a direction in which the second mounting member is pulled out in the axial direction from the first mounting member.
  • An apparatus wherein a diaphragm is attached to the first mounting member so as to face the vibration-proof substrate, and a liquid sealing chamber is provided between the vibration-proof substrate and the diaphragm inside the first mounting member.
  • the enclosing chamber is partitioned by a partition into a main liquid chamber on the vibration-isolating base side and a sub-liquid chamber on the diaphragm side, and both liquid chambers are connected via an orifice.
  • the volume of both liquid chambers changes in a direction that can be relatively varied due to the elastic deformation of the vibration base. It consists of a piston-like member and a cylinder-like member surrounding the outer periphery of the piston-like member.
  • the MR fluid whose viscosity changes according to the magnetic field strength is sealed between the piston-like member and the cylinder-like member in a flowable state.
  • An MR flow path for holding is formed, and an electromagnet capable of controlling a magnetic field strength for forming a magnetic path crossing the MR flow path and changing the viscosity of the MR fluid is provided.
  • the piston-like member in the liquid filled type vibration damping device of the present invention, by turning on / off the energization of the electromagnet or controlling the energization current to increase or decrease the viscosity of the MR fluid, the piston-like member can be fixed at a fixed position, The volume of the liquid chamber and the sub-liquid chamber can be displaced in a direction that can be relatively varied, thereby controlling and controlling the dynamic panel constant and damping coefficient of the vibration isolator. The anti-vibration performance can be exhibited.
  • the suspension type vibration damping device since the suspension type vibration damping device is used, the auxiliary liquid chamber on the diaphragm side expands when excessive displacement in the direction in which the supporting load exerts.
  • the MR flow path is orthogonal to the displacement direction so that the flow path portions located parallel to each other along the displacement direction of the piston-like member and the flow path portions communicate with each other.
  • it is preferably formed to have a crank-shaped cross section having a flow path portion that is located along a direction substantially orthogonal to and forms a transverse portion of the magnetic path.
  • the flow path of the MR fluid has a crank-shaped cross section and the magnetic path crosses the flow path portion of the crank-shaped flow path that is substantially perpendicular to the displacement direction of the piston-like member.
  • the flow of the MR fluid can be blocked and the rigidity of the piston-like member can be rapidly increased.
  • the MR fluid depends on the internal frictional force of the MR fluid, which increases in viscosity with energization.
  • FIG. 1 is a longitudinal sectional view of a liquid filled type vibration damping device according to one embodiment of the present invention
  • Fig. 2 is an enlarged sectional view of the main part of the vibration isolator
  • FIG. 3 is a graph showing the relationship between the frequency, the dynamic spring constant and the damping coefficient of the vibration isolator
  • FIG. 4 is a longitudinal sectional view of a conventional liquid-filled vibration isolator.
  • the anti-vibration device of the present embodiment is an engine mount that supports an automobile engine in an anti-vibration manner, and includes a cylindrical first metal mounting member 10 mounted on a vehicle body side and an inner axial center.
  • a metal second mounting member 12 disposed on the engine side and mounted on the engine side, and a vibration-proof base 14 made of a rubber material interposed between the mounting members 10 and 12 and connecting the two.
  • a suspension-type liquid-filled type vibration damping device comprising a second mounting member 12 and a supporting load applied in a direction in which the second mounting member 12 is drawn downward in the axial direction from the first mounting member 10.
  • the vibration-proof base 14 has a substantially truncated conical outer shape, and a substantially cylindrical second mounting member 12 is embedded so as to penetrate the center axis thereof.
  • the outer periphery of the lower end is adhesively fixed to the inner peripheral surface of the lower part of the first mounting member 10 by vulcanization molding means.
  • the first mounting member 10 is formed by fastening the upper cylindrical member 16 and the lower cylindrical member 18 at both ends by caulking, and the lower cylindrical member 18 is provided with the second mounting member 18.
  • the member 12 is fitted into the cup-shaped bracket 22 having an opening 20 through which the member 12 is fitted.
  • a flexible diaphragm 24 made of a thin rubber film is attached to the upper end opening of the first mounting member 10 so as to face the vibration isolating base 14.
  • a liquid filling chamber 26 sealed between the diaphragm 24 and the vibration-proof base 14 is formed, and the first mounting inside the liquid filling chamber 26 is formed.
  • a disk-shaped partition portion 30 forming an orifice 28 on the outer periphery is liquid-tightly fitted on the inner periphery of the member 10.
  • the liquid filling chamber 26 is vertically partitioned by the partition 30.
  • a main liquid chamber 32 in which a part of the chamber wall is formed by the vibration-proof base 14 is provided on the vibration-proof base side of the partition 30, that is, on the lower side, and the diaphragm side of the partition 30, that is, On the upper side, a sub-liquid chamber 34 in which a part of the chamber wall is formed by a diaphragm 24 is provided, and the two liquid chambers 32 and 34 are connected via an orifice 28.
  • the partition part 30 is a disk that can be displaced in the direction in which the volumes of the two liquid chambers 32 and 34 are relatively varied in accordance with the elastic deformation of the vibration isolating base 14 when vibration is applied, that is, in the vertical direction (axial direction).
  • the orifice 28 is formed on the outer periphery of the cylindrical member 38. I have.
  • an MR flow path 42 for hermetically holding the MR fluid 40, whose viscosity changes according to the magnetic field strength, in a flowable state.
  • the MR flow path 42 is provided over the entire circumference by a thin cover rubber 44 attached between the outer peripheral portion of the piston-like member 36 and the inner peripheral portion of the cylindrical member 38.
  • the piston-like member 36 forms a magnetic path mp that traverses the MR flow path 42 and is an annular coil capable of controlling the magnetic field strength for changing the viscosity of the MR fluid 40.
  • An electromagnet 46 composed of: a bobbin 48 holding the electromagnet 46; and a case 52 holding the bobbin 48 so as to be sandwiched vertically using fastening bolts 50.
  • the outer peripheral surface of the case 52 is cut out over the entire circumference, whereby the piston-like member 36 is formed in a short cylindrical shape having a concave portion 54 extending in the circumferential direction on the outer peripheral surface.
  • the cylindrical member 38 is made of a non-magnetic or weak magnetic material, and an inner peripheral surface thereof is provided with an annular yoke portion 56 made of a ferromagnetic material protruding toward the inner biston-shaped member 36. I have.
  • the MR flow path 42 is composed of a pair of upper and lower vertical flow paths 42 A, 42 A and an intermediate vertical flow path located parallel to each other along the relative displacement direction of the piston-like member 36 and the cylinder-like member 38.
  • the portion 42B and the pair of upper and lower vertical flow passages 42A, 42A and the intermediate flow passage portion 42B in a direction orthogonal or substantially orthogonal to the relative displacement direction so as to communicate with each other. It has a pair of upper and lower horizontal flow passage portions 42 C, 42 C located along the same, and is formed in a crank shape in cross section as a whole.
  • a passage 42 having a crank-shaped cross section is formed by inserting the inner peripheral end of the yoke portion 56 of the cylindrical member 38 into the concave portion 54 of the piston member 36 from the outside thereof.
  • the vertical flow path portions 42A and 42A are provided on both upper and lower sides of the yoke portion 56, respectively, and an intermediate vertical flow path portion 42B is provided along the inner peripheral end of the yoke portion 56.
  • Horizontal flow path portions 42 C and 42 C communicating these components are provided along the upper and lower surfaces of the yoke portion 56.
  • the electromagnet 46 crosses a pair of upper and lower horizontal flow paths 42 C and 42 C of the MR flow path. It is arranged inside the concave portion 54 of the biston-shaped member 36 so as to form a magnetic path mp as follows.
  • a lead wire 58 is connected to the electromagnet 46, and the lead wire 58 is connected to the control unit 60.
  • an opening is provided at the center of the diaphragm 24, the peripheral edge 24A of the opening is connected to the upper surface of the piston-like member 36, and the lead wire 58 is drawn out from the inside of the connecting portion.
  • the lead wire 58 is connected without passing through the liquid chamber 34.
  • the diaphragm 24 is formed in a bellows-like cross section having a middle bent portion 24B which is folded in a direction toward the partition portion 30, that is, downward so as to secure a bending allowance.
  • the MR fluid 40 is a Bingham fluid in which ferromagnetic metal particles having a particle diameter of about 1 to 10 / m are dispersed in a high-concentration suspension. It has an operating temperature range of C and its viscosity changes according to the magnitude of the magnetic field strength. It is called a magnetorheological fluid or a magnetorheological fluid.
  • the vibration damping device of the present embodiment configured as described above, when the power to the electromagnet 46 is turned on, the viscosity of the MR fluid 40 increases, and the piston-like member 36 becomes hard to be displaced and is fixed at a fixed position. You. On the other hand, when the energization of the electromagnet 46 is turned off, the viscosity of the MR fluid 40 decreases, and the piston-like member 36 is easily displaced, and the displacement causes the main liquid chamber 32 and the sub liquid chamber 34 to move. Can be varied. Further, by adjusting the viscosity of the MR fluid 40 by controlling the energizing current, the vibration can be attenuated by the viscous effect of the MR fluid 40.
  • the resonance frequency of the orifice 28 is ⁇ Make settings so as to attenuate vibrations (for example, around 12 Hz) and idle vibrations (for example, 15 to 21012) when power is on.
  • idle vibration of 17 Hz can be attenuated by the orifice 28.
  • the resonance frequency of the orifice 28 decreases to about 12 Hz, so that the shake vibration can be attenuated.
  • Vibration damping effect can be exerted against vibrations in a high frequency range exceeding 20 Hz (for example, 40 to 300 Hz). By performing such control, it is possible to reduce the amount of electric power consumed while the vehicle is running, and to contribute to a reduction in fuel consumption of the entire vehicle.
  • the control method is not limited to the above, and may be controlled, for example, as follows. Under the condition where vibrations in the low frequency range are applied, energization is turned on, the piston-like member 36 is fixed in place, and the orifice 28 is connected between the main liquid chamber 32 and the sub liquid chamber 34. The liquid is caused to flow to absorb fluctuations in the liquid pressure in the main liquid chamber 32, thereby attenuating vibration in the low frequency region. Then, under the condition where the vibration in the high frequency region acts, the energization is turned off, or the energization current is increased or decreased to adjust the magnitude of the magnetic field strength, thereby reducing the dynamic panel constant of the piston-like member 36. Makes it smaller than when energized, and exhibits a vibration proof effect against vibrations in the high frequency range.
  • the liquid-filled type vibration damping device of the present embodiment can exhibit the vibration damping performance in a wide frequency range, but also has improved durability of the diaphragm 24.
  • the support load is excessively displaced in the direction in which the supporting load is exerted (the direction in which the second mounting member 12 moves downward, that is, the direction in which the main liquid chamber 32 expands)
  • Sub liquid chamber 3 4 is not in the expansion direction, so the partition

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Combined Devices Of Dampers And Springs (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)

Abstract

Cette invention concerne un dispositif d'isolation des vibrations hydraulique de type à suspension dans lequel : une pression de soutènement est exercée sur un second élément d'installation (12) placé à l'intérieur d'un premier élément d'installation tubulaire (10) dans un sens tel que l'élément (12) est extrait dans un sens axial ; une partie de séparation (30) servant à séparer un compartiment de liquide principal (32) inférieur d'un compartiment de liquide auxiliaire (34) supérieur est composée d'un élément de type piston (36) et d'un élément de type cylindre (38) pouvant se déplacer pour que les volumes des deux compartiments de liquide (32, 34) varient en fonction de la déformation élastique d'un corps de base d'isolation des vibrations (14) lorsqu'une vibration est appliquée sur celui-ci afin qu'un effet d'isolation des vibrations soit développé dans une vaste gamme de fréquences ; un fluide à résonance magnétique (40) présentant une viscosité variable en fonction de l'intensité d'un champ magnétique est contenu de façon étanche entre l'élément de type piston (36) et l'élément de type cylindre (38) ; et un électroaimant (46) pouvant commander l'intensité du champ magnétique est installé dans l'élément de type piston.
PCT/JP2003/004584 2003-01-29 2003-04-10 Dispositif d'isolation des vibrations hydraulique WO2004067992A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2003236069A AU2003236069A1 (en) 2003-01-29 2003-04-10 Liquid-seal vibration isolating device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2003-21194 2003-01-29
JP2003021194A JP2004232708A (ja) 2003-01-29 2003-01-29 液体封入式防振装置

Publications (1)

Publication Number Publication Date
WO2004067992A1 true WO2004067992A1 (fr) 2004-08-12

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PCT/JP2003/004584 WO2004067992A1 (fr) 2003-01-29 2003-04-10 Dispositif d'isolation des vibrations hydraulique

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JP (1) JP2004232708A (fr)
AU (1) AU2003236069A1 (fr)
WO (1) WO2004067992A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106904068A (zh) * 2017-05-08 2017-06-30 牛艳兵 一种汽车发动机悬置装置

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101184283B1 (ko) 2010-11-30 2012-09-21 현대자동차주식회사 Ｍｒ유체가 봉입된 댐핑제어장치 및 상기 댐핑제어장치를 구비한 엔진마운트
KR101298267B1 (ko) 2011-08-01 2013-08-22 현대자동차주식회사 Ｍｒ유체가 봉입된 엔진마운트용 오리피스플레이트
KR101773521B1 (ko) * 2016-04-08 2017-08-31 평화산업주식회사 벤트홀을 포함하는 능동형 엔진마운트
KR102500776B1 (ko) 2017-01-20 2023-02-17 티센크루프 스틸 유럽 악티엔게젤샤프트 주로 베이나이트 미세조직을 갖는 복합조직상 강으로 구성된 열연 평탄형 강 제품 및 이러한 평탄형 강 제품을 제조하는 방법
KR102575424B1 (ko) * 2018-08-20 2023-09-05 현대자동차주식회사 자동차용 액티브 엔진 마운트

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04334625A (ja) * 1991-05-10 1992-11-20 Tokai Rubber Ind Ltd 流体封入式吊下げ型マウントに対する取付部材の組付方法
JP2002206591A (ja) * 2001-01-12 2002-07-26 Toyo Tire & Rubber Co Ltd 液体封入式防振装置
JP2002206585A (ja) * 2001-01-12 2002-07-26 Toyo Tire & Rubber Co Ltd 液体封入式振動吸収装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04334625A (ja) * 1991-05-10 1992-11-20 Tokai Rubber Ind Ltd 流体封入式吊下げ型マウントに対する取付部材の組付方法
JP2002206591A (ja) * 2001-01-12 2002-07-26 Toyo Tire & Rubber Co Ltd 液体封入式防振装置
JP2002206585A (ja) * 2001-01-12 2002-07-26 Toyo Tire & Rubber Co Ltd 液体封入式振動吸収装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106904068A (zh) * 2017-05-08 2017-06-30 牛艳兵 一种汽车发动机悬置装置
CN106904068B (zh) * 2017-05-08 2018-01-23 牛艳兵 一种汽车发动机悬置装置

Also Published As

Publication number Publication date
AU2003236069A1 (en) 2004-08-23
JP2004232708A (ja) 2004-08-19

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