WO2002025138A1 - Isolateur de vibration - Google Patents

Isolateur de vibration Download PDF

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Publication number
WO2002025138A1
WO2002025138A1 PCT/JP2001/007621 JP0107621W WO0225138A1 WO 2002025138 A1 WO2002025138 A1 WO 2002025138A1 JP 0107621 W JP0107621 W JP 0107621W WO 0225138 A1 WO0225138 A1 WO 0225138A1
Authority
WO
WIPO (PCT)
Prior art keywords
vibration
cross
rubber elastic
outer cylinder
elastic body
Prior art date
Application number
PCT/JP2001/007621
Other languages
English (en)
Japanese (ja)
Inventor
Yoshio Ihara
Masashi Takaoka
Hironori Kato
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 JP2002528706A priority Critical patent/JP3661060B2/ja
Publication of WO2002025138A1 publication Critical patent/WO2002025138A1/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
    • F16F1/00—Springs
    • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
    • F16F1/38—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type
    • F16F1/387—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type comprising means for modifying the rigidity in particular directions
    • F16F1/3873—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type comprising means for modifying the rigidity in particular directions having holes or openings

Definitions

  • the present invention relates to an anti-vibration device mainly used as an engine mount, a suspension bush or the like of an automobile.
  • a device in which an inner cylinder and an outer cylinder are connected by a rubber elastic body interposed between the two brackets has been known.
  • the inner cylinder is attached to one of the support members having a substantially U-shape via a shaft member to be fitted into the inner cylinder, and the outer cylinder is attached to the other support member such as a bracket. Pressed and fixed.
  • These support members are provided on a vibration source such as an engine and a support side such as a vehicle body, respectively.
  • FIG. 21 shows a conventional example of such a vibration isolator.
  • the rubber elastic body 103 interposed between the inner cylinder fitting 101 and the outer cylinder fitting 102 has hollow portions 10 above and below the inner cylinder fitting 101, respectively. 4, 105, and the lower cavity portion 105 has an upper portion 106 protruding upward.
  • the convex portion 106 is abutted against the ceiling surface 151 of the lower hollow portion 105 in a state of receiving a load while supporting an engine or the like. Therefore, the rubber elastic body 103 supports the inner cylinder fitting 101 from both the left and right sides when the axial direction is the front-rear direction. Supports the bracket 101. That is, the convex portion 106 shares a certain load.
  • the inner cylinder fitting 101 is disposed substantially at the center of the cross-sectional shape of the outer cylinder fitting 102.
  • the outer cylinder 102 has a substantially elliptical or oval cross section, and its major axis is oriented in the horizontal direction (Y direction).
  • Y direction the horizontal direction
  • the outer cylinder fitting 102 when used with the axial direction of the cylindrical vibration isolator set to the front and rear directions (X direction) with respect to the vehicle, a substantially elliptical cross section that is long in the left-right direction (Y direction). Having. This is because the inner cylinder fitting 101 needs to be supported by a sufficient amount of rubber elastic material from the left and right, and the stability of the vibration-proofing properties and the like.
  • the above-mentioned vibration isolator is usually designed such that the convex portion comes into contact with the ceiling surface of the lower cavity portion at the time of a basic load in which the engine is supported and stood still from the vehicle body.
  • the dynamic spring constant in the vertical direction (Z direction) tends to be high. If the dynamic panel constant becomes too high, problems such as insufficient vibration isolation characteristics for relatively small amplitude vibrations will occur.
  • the width of the convex portion 106 (dimension in the Y direction in Fig. 12) is entirely reduced in order to reduce the dynamic panel constant appropriately, the dynamic panel in the vertical direction (Z direction) of the entire vibration isolator
  • the contribution ratio (sharing ratio) of the convex portion 106 in the constant changes.
  • the position of the inner cylinder fitting 101 at the time of the basic load that is, the position for supporting the engine changes.
  • the panel force when the convex portion 106 acts as a stopper panel for restricting large deformation is reduced, the stroke when receiving vibration becomes excessive.
  • the deflection value corresponding to the load at a given vibration peak shifts to the side of large deformation when viewed from the load-deflection curve.
  • the present invention has been made in view of the above-mentioned problems, and has an inner cylindrical member and an outer cylindrical member.
  • the rubber elastic body is an anti-vibration mount having cavities above and below the inner cylindrical metal fitting, and projects downward into the lower cavity part under load.
  • a device provided with a convex portion with which a ceiling surface of a hollow portion abuts, and capable of appropriately reducing a dynamic panel constant in a vertical direction without deteriorating durability.
  • An anti-vibration device is characterized in that an inner cylinder and an outer cylinder arranged to surround the outer cylinder are connected by a rubber elastic body interposed between the inner and outer brackets.
  • the rubber elastic body has an upper cavity portion and a lower cavity portion above and below the inner cylinder, and protrudes from the side of the outer cylinder toward the upper inner cylinder in the lower cavity.
  • a vibration isolator wherein a convex portion is provided, and a ceiling surface of the lower cavity portion abuts on a distal end surface of the convex portion under a load of a predetermined value or more, wherein a small cavity is provided in the convex portion. It is characterized by.
  • the convex portion is more likely to be elastically deformed than a convex portion having no small cavity in a certain amplitude range due to the existence of the small cavity, thereby reducing the vertical dynamic panel constant.
  • the small cavity is crushed and the wall is brought into close contact with each other, so that the spring force of the stopper spring for regulating large deformation is increased, and a good stopper action is achieved. Therefore, the dynamic panel constant in the vertical direction can be reduced without lowering the durability, and good and sufficient anti-vibration characteristics can be maintained even when the vibration has a small amplitude.
  • the outer cylinder has an approximately elliptical cross section that is long horizontally, and the inner cylinder is eccentrically arranged upward with respect to the outer cylinder in a no-load state, and the rubber elasticity is provided. It is preferable that the body supports the inner cylinder from both left and right sides in the cross section of the outer cylinder. Accordingly, when the axial direction of the vibration isolator is the front-back direction, the inner cylinder fitting is supported by a sufficient amount of rubber elastic body from the left and right by having a substantially elliptical cross section that is long in the left-right direction. Characteristics become stable.
  • the small cavity in the projection may be a through hole in the axial direction or a non-through hole in the axial direction. Also, a plurality of small cavities can be provided in the projection.
  • the rigidity of the convex portion can be appropriately set according to the diameter, shape, number and the like of these holes.
  • FIG. 1 is a cross-sectional view (cross-sectional view taken along line C--C1 in FIG. 3) of the cylindrical anti-vibration mount 10 of the first embodiment cut along the axial center at a no-load state.
  • FIG. 2 is a cross-sectional view (a cross-sectional view taken along line Bl-B1 in FIG. 1) of the anti-vibration mount 10 of Example 1 so as to be equally divided into left and right when viewed from the axial direction. In particular, it shows a state where it is attached to the support member from above and below.
  • FIG. 3 is a cross-sectional view of the anti-vibration mount 10 according to the first embodiment cut along the left and right sides of the small cavity 61 in the convex portion 6 (cross-sectional view taken along the line A1-A1 in FIG. 1). ).
  • FIG. 4 is a front view (as viewed from the left side in FIGS. 2 and 3) of the anti-vibration mount 10 of the first embodiment when pressed into the support member 30.
  • FIG. 5 is a cross-sectional view corresponding to FIG. 1 showing a state under a standard load with respect to the vibration isolating mount 10 of the first embodiment.
  • FIG. 6 is a cross-sectional view corresponding to FIG. 1 of the anti-vibration mount of the second embodiment.
  • FIG. 7 is a cross-sectional view corresponding to FIG. 2 of the anti-vibration mount of the second embodiment.
  • FIG. 8 is a sectional view corresponding to FIG. 3 of the anti-vibration mount of the third embodiment. is there.
  • FIG. 9 is a cross-sectional view corresponding to FIG. 1 of the anti-vibration mount of the fourth embodiment.
  • FIG. 10 is a sectional view corresponding to FIG. 1 of the anti-vibration mount of the fifth embodiment.
  • FIG. 11 is a cross-sectional view corresponding to FIG. 1 of the anti-vibration mount of the sixth embodiment.
  • FIG. 12 is a cross-sectional view of the circular anti-vibration mount 10 according to the seventh embodiment, which is cut at the center in the axial direction. Shows the state without load.
  • FIG. 13 is a cross-sectional view of the vibration isolator in which small cavities are provided on both sides of the rubber elastic body, taken along line A2-A2 in FIG. 14 in a no-load state.
  • FIG. 14 is a cross-sectional view taken along the line B2-B2 in the previous figure.
  • FIG. 15 is a cross-sectional view taken along line C2-C2 in FIG.
  • FIG. 16 is a sectional view taken along the same line as FIG. 3 showing another embodiment.
  • FIG. 17 is a partial cross-sectional view showing another example of the small cavity.
  • FIG. 18 is a partial cross-sectional view showing still another example of the small cavity.
  • FIG. 19 is a partial cross-sectional view showing still another example of the small cavity.
  • FIG. 20 is a cross-sectional view showing another embodiment of the vibration isolator in which the outer metal fitting is substantially elliptical.
  • Fig. 21 is a cross-sectional view corresponding to Fig. 1 of the conventional anti-vibration mount.
  • the anti-vibration device is an anti-vibration mount for an engine that supports an engine by suspending the engine from a support member on a vehicle body side of an automobile.
  • Figure 1 shows a cylindrical protection
  • FIG. 4 is a cross-sectional view (a cross-sectional view taken along line C 1 -C 1 in FIG. 3) of the vibration mount 10 cut at a central portion in the axial direction.
  • Fig. 2 is a cross-sectional view of the anti-vibration mount 10 that is cut equally to the left and right when viewed from the axial direction (a cross-sectional view taken along the line B1-B1 in Fig. 1). It is sectional drawing cut
  • FIG. 2 particularly shows the anti-vibration mount 10 mounted on the support members 30 and 40 from above and below.
  • Fig. 3 is a cross-sectional view similar to Fig. 2 (a cross-sectional view taken along the line A1-A1 in Fig. 1) when cut slightly off the left and right symmetry lines
  • Fig. 4 is a cross-sectional view of Figs. 5 is a front view of the anti-vibration mount 10 viewed from the left side of FIG.
  • FIG. 5 is a cross-sectional view similar to FIG. 1 showing a deformed state under a standard load.
  • the anti-vibration mount 10 is composed of an inner cylinder 1 having a relatively thick cylindrical shape and an outer cylinder 2 arranged so as to surround the outer cylinder 1. And are connected by a rubber elastic body 3.
  • the rubber elastic body 3 is integrally formed by rubber vulcanization molding and is adhered to the inner cylinder 1 and the outer cylinder 2.
  • the outer surface of the inner cylindrical member 1 has a rectangular shape slightly longer in the transverse direction near the axial center of the anti-vibration mount 10 in a cross section perpendicular to the axial direction, but has a circular shape in other places. That is, the inner cylinder 1 has a “bulge” that protrudes outward in a square shape near the center in the axial direction. Meanwhile, the inner tube fitting
  • the inner surface of 1 is a cylinder having a uniform diameter as a whole so as to receive the cylindrical shaft member 41.
  • the columnar shaft member 41 is supported from the upper vehicle body side by a U-shaped support member 40 having a cross section that is inclined sideways.
  • the outer tube 2 has a slightly smaller axial (X direction) dimension than the inner tube 1 as shown in Figs. 2-3, and as shown in Fig. 1, the cross section perpendicular to the axial direction (Y direction) as the major axis. are doing.
  • the outer cylinder fitting 2 is press-fitted into a horizontal mounting hole provided in the lower support member 30.
  • the lower support member 30 suspends the engine when the anti-vibration mount 10 is used.
  • the anti-vibration mount 10 When the anti-vibration mount 10 is not loaded, that is, when no load is applied between the inner cylinder 1 and the outer cylinder 2, as shown in Fig. 1 etc., the inner cylinder 1 is attached to the outer cylinder. It is arranged eccentrically upward with respect to 2.
  • the rubber elastic body 3 that fills the space between the inner cylinder 1 and the outer cylinder 2 has cavities 4 and 5 formed with through holes in the axial direction above and below the inner cylinder 1.
  • both side portions 3 a and 3 b as support arms of the rubber elastic body 3 are in a state of supporting the inner cylindrical member 1 from both left and right sides in a cross section of the outer cylindrical member 2.
  • These cavities 4 and 5 have a bow shape bulging upward in a cross section perpendicular to the axial direction (the cross section in the left-right direction in FIG. 1), and are wide at both ends.
  • the upper cavity 4 extends slightly from the inner surface of the outer tube fitting 2, and the lower cavity 5 has an upper end slightly above the lower surface of the inner tube 1. They are placed apart.
  • the lower surface of the lower cavity 5 protrudes from the side of the outer cylinder 2 toward the upper inner cylinder 1, thereby forming a convex portion 6 as a stopper 1 for restricting downward displacement. It is formed integrally with the elastic body 3.
  • the convex portion 6 has a substantially trapezoidal shape in both the left-right direction (Y direction) cross section and the axial direction (X direction, front-rear direction) cross section. Therefore, the upper end surface 6a of the convex portion 6 forms a horizontal flat surface at the central portion in the axial direction.
  • the upper end surface 6a of the convex portion is separated from the ceiling surface 51 of the lower cavity portion 5 at a slight interval when the load is not applied, by the entire surface being flat and horizontal.
  • the tip end surface of the projection 6, that is, the upper end surface 6 a comes into contact with the ceiling surface 51 of the lower cavity 5.
  • a plurality of grooves 6 b extending in the axial direction are provided on the outer surface of the convex portion 6 and are provided along the symmetry line of the convex portion 6.
  • the upper end surface 6a of the convex portion is not a completely flat surface but has some irregularities. Even if the upper end surface 6a of the convex portion has another uneven shape, for example, a wavy shape as a whole, or the width and depth dimensions of the groove 6b are larger, it will be described later. The effect is almost the same.
  • the small cavity 61 is a cylindrical through-hole having a uniform diameter in the axial direction, as can be seen from the cross-sectional views of FIGS. 1 and 3 (cross-section taken along line A 1 -A 1 in FIG. 1).
  • the dynamic panel constant in the up-down direction (Z direction) of the anti-vibration mount 10 could be easily reduced.
  • the convex portion 6 Due to the existence of the small cavities 61, elastic deformation is more likely to occur up to a certain deformation range compared to the convex portion 6 having no small cavities, which can lower the vertical dynamic panel constant. it can. Moreover, at the time of vibration having a large amplitude, the small cavity 61 is crushed and its wall surface comes into close contact with each other, so that the panel force as a stopper panel for controlling large deformation is increased, and a good stopper effect is achieved. Therefore, without lowering durability, The dynamic panel constant in the direction can be reduced.
  • Kd15 the dynamic panel constant in the vertical direction (Z direction) at 15 Hz
  • the load shared by the protrusions 6 is maintained at 157 ON, which is the same as that of the conventional example, by slightly increasing the width (the dimension in the left-right direction) of the protrusions 6.
  • the shared load of the convex portion 6 can be maintained, even if the dynamic panel constant is reduced, the relative position between the inner cylindrical member 1 and the outer cylindrical member 2 at the time of load is changed, and the stroke due to vibration is reduced. It does not increase. Therefore, even if the dynamic panel constant is reduced, the durability of the anti-vibration mount 10 is not impaired.
  • the load of the convex portion 6 decreased from 1570 N to 1250 N, although the load was reduced from 1570 N to 1250 N.
  • the lowering of the dynamic spring constant in the vertical direction at 5 Hz and 100 Hz was 11% and 10%, respectively.
  • rubber stoppers 7, 8 projecting in the axial direction.
  • the rubber stoppers 7 and 8 each have outer edges 7 a and 8 a which protrude outward in the axial direction and then extend downward, and abutment surfaces 7 b and 8 b against the upper support member 40. 8b.
  • the rubber stopper portions 7 and 8 play a role of preventing interference between metals.
  • the dynamic spring constant in the vertical direction of the anti-vibration mount can be maintained without changing the shared load of the convex portion 6 only by providing the small cavity 61 in the convex portion 6. Can be greatly reduced.
  • the shape, size, number, arrangement, and the like of the small cavities 61 provided in the convex portions 6 can be variously changed according to the required dynamic panel constant, vibration-proof characteristics, and the like.
  • the small cavity 61 in this modified example has a circular cross-sectional shape whose center is located on the line of symmetry with respect to the left-right direction (the line D-D in FIG. 6). The diameter gradually decreases toward.
  • Example 3 shown in FIG. 8 in the same configuration as that of Example, the small cavity 61 in the convex portion 6 is formed by a non-through hole. That is, the structure is such that the two through holes in the embodiment are closed at the axial center.
  • the cross section of the two small cavities 61 as the through holes has a triangular shape with rounded corners.
  • the small cavity 61 provided as a through-hole has a single, long, right and left, flat elliptical cross section.
  • a small cavity 61 is provided as one through hole 61a that is located on the left-right symmetry line and has a substantially elliptical cross section that is long in the vertical direction, and is provided symmetrically below it.
  • two through holes 61b having a circular cross section.
  • the outer metal fitting 2 has a case where the cross section has a substantially oval shape or an oval shape having a horizontally long cross section. As shown in Embodiment 7, the same can be applied to a case where the cross-section of the outer cylinder 2 is circular.
  • the upper elastic portion 4 and the lower concave portion 5 are provided in the rubber elastic body 3 interposed between the outer cylindrical fitting 2 and the inner cylindrical fitting 1, and the lower cavity portion is provided.
  • 5 is provided with a convex portion 6 projecting upward from the side of the outer metal fitting 2 and contacting the ceiling surface 51 of the lower cavity portion 5 under a constant load.
  • the small cavities 61 similar to those in the above-described embodiment are provided in the convex portions 6.
  • the shape, size, number, arrangement, and the like of the small cavities 61 can be variously changed. In this case, the same effect as above can be exerted.
  • the inner cylinder and the outer cylinder are both mounted.
  • the inner cylinder 1 is supported on the left and right sides with respect to the outer cylinder 2 in order to reduce the dynamic panel constant in the horizontal direction perpendicular to the axis.
  • small cavities 3 la,. 3 b are provided on both sides 3 a, 3 b of the rubber elastic body 3.
  • substantially the same components as those in Embodiments 1 to 7 described above are denoted by the same reference numerals. .
  • the basic structure of the vibration isolator of these embodiments is also substantially the same as that of the above-described embodiment, and has the following structure.
  • a relatively thick cylindrical inner cylinder 1 and an outer cylinder 2 surrounding the outer cylinder are formed by a rubber elastic body 3 interposed between the inner and outer cylinders.
  • the rubber elastic body 3 is integrally formed by vulcanization molding and is adhered to the inner cylinder 1 and the outer cylinder 2.
  • the rubber elastic body 3 is provided with cavities 4 and 5 which are vertically opposed to each other with the inner cylindrical fitting 1 therebetween and have a required width in the circumferential direction.
  • the upper and lower cavities 4, 5 are each formed in a cross section perpendicular to the axial direction.
  • the upper and lower cavities 4, 5 are circumferentially wider than the outer diameter of the inner cylindrical fitting 1, and both side portions 3 a, 3 b of the rubber elastic body 3, which are elongated in a direction perpendicular to the axis, between the upper and lower cavities 4, 5 serve as support arms.
  • the inner tube 1 is provided so as to be supported at a substantially central portion with respect to the outer tube 2.
  • the upper cavity 4 is formed slightly wider than the lower cavity 5, and the rubber elastic body 3 has both sides 3 a, 3 b as supporting arms formed of outer cylinder fittings 2. It is bonded to the inner surfaces of the front and rear sides of the front and rear sides slightly downward from the middle in the vertical direction, and has a mountain shape with the center bulging upward.
  • the inner cylindrical member 1 fixed to the central portion of the rubber elastic body 3 is disposed eccentrically upward with respect to the outer cylindrical member 2 in a no-load state, so that a predetermined load such as a power unit is applied. In the loaded state, it is supported substantially coaxially with the outer tube fitting 2 as shown by the chain line in FIG. 13 so as to maintain a predetermined clearance up and down.
  • a convex part 1 for stopper having a predetermined thickness is provided on the side of the outer tube fitting 2 of the upper and lower cavities 4, 5, that is, on the upper surface of the upper cavity 4 and the lower surface of the lower cavity 5, a convex part 1 for stopper having a predetermined thickness is provided.
  • 6 and 17 are integrally formed by vulcanization using the same rubber as the rubber elastic body 3, and when the vertical vibration is input by the amplitude of the inner cylinder 1 being larger than a certain level, the upper and lower surfaces of the inner cylinder 1 are input.
  • the rubber elastic body 3 is provided so as to contact the stopper projections 16 and 17 to restrict the movement.
  • Each of the side portions 3a and 3b of the rubber elastic body 3 has a position slightly inward from the outer cylinder 2 and preferably an intermediate position between the inner cylinder 1 and the outer cylinder 2. Small cavities 18 and 18 are provided near the point.
  • the small cavities 18, 18 are formed of circular holes in the axial direction, and in particular, as shown in FIG. 15, formed of non-through holes in the axial direction formed while leaving the non-penetrated portion 18 a.
  • it may consist of an axial through hole.
  • the position of the unpenetrated portion 18 a is set at a substantially central portion in the axial direction, and is formed at one end in the axial direction or at one end thereof. It can also be formed so as to leave an unpenetrated portion 18a in the vicinity.
  • the diameter, cross-sectional shape, size, depth and number of the small cavities 18 can be variously changed according to the required rigidity and dynamic spring constant in both cases of non-through holes and through holes. It is.
  • small cavities 18 consisting of multiple holes (two holes in the figure) as shown in Fig. 17 can be arranged side by side at required intervals, or a round cross section as shown in Fig. 18
  • the hole may be a substantially triangular hole or a hole having a flat cross section as shown in FIG. 19, and these holes may be arranged in combination. In both the case of the non-through hole and the case of the through hole, it is not necessary to have the same diameter and the same shape inward in the axial direction from the opening end. .
  • the small elastic cavity 18 has no small cavity in both sides 3 a and 3 b as the supporting arms of the rubber elastic body 3. Tuning of rigidity is easily possible. In particular, when the small cavities 18 are non-through holes, the rigidity is set higher than that of the case where the small cavities 18 are non-through holes due to the presence of the non-through holes 18a. By adjusting or changing the hole depth, that is, the wall thickness of the unpenetrated portion 18a, the tuning of the rigidity can be easily performed. As a result, the degree of freedom in design is expanded.
  • the upper cavity 4 and the lower cavity 4 are formed.
  • the side cavity 5 it can be made of a core.
  • a portion corresponding to the small cavity may be hollowed out. In any case, it can be provided by a simple work process O
  • the inner cylinder 1 is attached to one of the support members on the power unit side and the vehicle body side via a shaft member inserted therein, and the outer cylinder 2 is Press-fit into the mounting hole of the other support member, such as a bracket, or the like, and fix it.
  • the axial direction (X direction) is set to the left and right direction with respect to the vehicle, and the power unit is used so as to regulate the vibration in the longitudinal direction.
  • the small cavities 8 are crushed by providing the axial small cavities 8 on both sides 3 a and 3 b as the support arms of the rubber elastic body 3.
  • the panel in the left and right direction becomes softer against vibrations below a certain amplitude up to the shape of the upper and lower cavities 4 and 5 without changing the outer shape of the side portions 3a and 3b, and the dynamic panel constant in the vertical direction
  • the dynamic spring constant in the front-rear direction which is the horizontal direction perpendicular to the axis, can be reduced without greatly affecting the vibration isolation characteristics, and the vibration isolation characteristics in the front-rear direction can be improved.
  • the small cavity 8 is provided at a position distant from the outer cylinder 2, particularly near an intermediate point between the inner and outer metal fittings 1 and 2, compression due to input of a vibration load in the front-rear direction.
  • heat generation in the vicinity of the intermediate point where heat is most likely to occur due to a large tensile movement can be effectively suppressed by the heat radiation effect of the small cavity 8.
  • the effect of heat dissipation is increased. As a result, a decrease in durability can be prevented.
  • the outer tube 2 is substantially circular in front.
  • the outer tube 2 is substantially elliptical in cross section, that is, It can be substantially elliptical with the longitudinal axis in the front-rear direction (Y direction).
  • the rubber elastic body 3 between the inner cylinder 1 and the outer cylinder 2 is used.
  • Both side portions 3 a and 3 b as support arms of 3 are provided so as to support the inner cylinder 1 with respect to the outer cylinder 2.
  • the upper cavity 4 is formed slightly wider than the lower cavity 5, and the center of the rubber elastic body 3 has a mountain shape bulging upward. ing.
  • the inner cylindrical member 1 fixed to the central portion of the rubber elastic body 3 is disposed eccentrically upward with respect to the outer cylindrical member 2 in a no-load state, so that a predetermined load such as a power unit is applied. In this state, it is supported substantially coaxially with the outer tube fitting 2 as shown by a chain line in FIG.
  • the lower cavity 5 is provided on the lower cylindrical portion 5 with respect to the convex stopper projection 17 provided on the outer cylinder fitting 2 side.
  • Ceiling surface 51 can be provided so as to abut.
  • small cavities can be provided in the convex portion 1 as in Examples 1 to 7.
  • Each of the side portions 3a and 3b as the supporting arms of the rubber elastic body 3 is located at a position slightly away from the outer cylinder 2 inward, preferably, the inner cylinder 1 and the outer cylinder 2. Near the midpoint between the small holes, small cavities 18 and 18 are provided which are formed of non-through holes or through holes in the axial direction. Various changes can be made to the small cavity 8 as in the above embodiment.
  • the shape of the upper and lower cavities 4 and 5 ⁇ without changing the outer shape of the side portions 3 a and 3 b and without significantly affecting the dynamic panel constant and the vibration isolation characteristics in the vertical direction.
  • the dynamic panel constant in the horizontal direction perpendicular to the axis can be reduced. Therefore, for example, when used with the axial direction set to the left-right direction, the anti-vibration characteristics in the front-rear direction can be improved.
  • horizontal vibration perpendicular to the axis Heat generation in the vicinity of the intermediate point where heat is most likely to be generated due to large compression and tension movements due to input of a dynamic load can be effectively suppressed by the heat radiation effect of the small cavity 18.
  • this anti-vibration device with the axial direction set to the front-rear direction of the vehicle, in which case the dynamic panel constant in the left-right direction can be reduced.
  • the anti-vibration device of the present invention can appropriately reduce the upward and downward dynamic spring constant without deteriorating durability, and thus is suitably used mainly as an engine mount for automobiles, suspension bushes, and the like. Can be used.

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  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Springs (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

La présente invention concerne un bâti (10) isolant des vibrations, qui comprend des barres (1, 2) métalliques cylindriques intérieure et extérieure connectées entre elles via un corps (3) élastique élastomère. Ce bâti possède des parties (4,5) creuses sur les côtés inférieur et supérieur de la barre métallique élastomère intérieure. Une partie (6) projection située dans la partie inférieure de la partie (5) creuse se projette vers le haut et permet à la surface (51) supérieure de la partie (5) creuse de venir toucher cette partie sous charge. Des petites cavités (61) comprenant des alésages axiaux traversent cette partie (6) projection, dans laquelle un ressort dynamique constamment vertical peut être abaissé de façon adaptée sans compromettre la durée de vie de ce bâti (10) isolant des vibrations.
PCT/JP2001/007621 2000-09-20 2001-09-03 Isolateur de vibration WO2002025138A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2002528706A JP3661060B2 (ja) 2000-09-20 2001-09-03 防振装置

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Application Number Priority Date Filing Date Title
JP2000-285580 2000-09-20
JP2000285580 2000-09-20

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WO2002025138A1 true WO2002025138A1 (fr) 2002-03-28

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006070440A1 (fr) * 2004-12-27 2006-07-06 Toyo Tire & Rubber Co., Ltd. Dispositif de maillon
WO2006077622A1 (fr) * 2005-01-18 2006-07-27 Toyo Tire & Rubber Co., Ltd. Amortisseur de vibrations
JP2010096277A (ja) * 2008-10-16 2010-04-30 Toyo Tire & Rubber Co Ltd 防振連結ロッド
EP3203108A4 (fr) * 2014-10-03 2017-12-06 Bridgestone Corporation Dispositif d'isolation de vibrations
CN113844223A (zh) * 2021-10-15 2021-12-28 安徽江淮汽车集团股份有限公司 一种车辆摆臂衬套

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60125430A (ja) * 1983-12-09 1985-07-04 Kinugawa Rubber Ind Co Ltd エンジンマウント用ブッシュ
JPS6327733U (fr) * 1986-08-08 1988-02-23
JPH0167342U (fr) * 1987-10-26 1989-04-28
JPH0248629U (fr) * 1988-09-30 1990-04-04
JPH09257075A (ja) * 1996-03-25 1997-09-30 Daihatsu Motor Co Ltd 合成樹脂製の防振マウント用ブラケット

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60125430A (ja) * 1983-12-09 1985-07-04 Kinugawa Rubber Ind Co Ltd エンジンマウント用ブッシュ
JPS6327733U (fr) * 1986-08-08 1988-02-23
JPH0167342U (fr) * 1987-10-26 1989-04-28
JPH0248629U (fr) * 1988-09-30 1990-04-04
JPH09257075A (ja) * 1996-03-25 1997-09-30 Daihatsu Motor Co Ltd 合成樹脂製の防振マウント用ブラケット

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006070440A1 (fr) * 2004-12-27 2006-07-06 Toyo Tire & Rubber Co., Ltd. Dispositif de maillon
WO2006077622A1 (fr) * 2005-01-18 2006-07-27 Toyo Tire & Rubber Co., Ltd. Amortisseur de vibrations
JP2010096277A (ja) * 2008-10-16 2010-04-30 Toyo Tire & Rubber Co Ltd 防振連結ロッド
EP3203108A4 (fr) * 2014-10-03 2017-12-06 Bridgestone Corporation Dispositif d'isolation de vibrations
US10337585B2 (en) 2014-10-03 2019-07-02 Bridgestone Corporation Vibration isolation device
CN113844223A (zh) * 2021-10-15 2021-12-28 安徽江淮汽车集团股份有限公司 一种车辆摆臂衬套

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