WO2005106283A1 - Dispositif isolateur de vibrations a liquide scelle - Google Patents

Dispositif isolateur de vibrations a liquide scelle Download PDF

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Publication number
WO2005106283A1
WO2005106283A1 PCT/JP2004/006399 JP2004006399W WO2005106283A1 WO 2005106283 A1 WO2005106283 A1 WO 2005106283A1 JP 2004006399 W JP2004006399 W JP 2004006399W WO 2005106283 A1 WO2005106283 A1 WO 2005106283A1
Authority
WO
WIPO (PCT)
Prior art keywords
orifice
liquid
partition
damping device
vibration damping
Prior art date
Application number
PCT/JP2004/006399
Other languages
English (en)
Japanese (ja)
Inventor
Masaaki Itoh
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 PCT/JP2004/006399 priority Critical patent/WO2005106283A1/fr
Priority to JP2006516829A priority patent/JP4212624B2/ja
Publication of WO2005106283A1 publication Critical patent/WO2005106283A1/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
    • F16F13/06—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
    • F16F13/10—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 the wall being at least in part formed by a flexible membrane or the like
    • F16F13/105—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 the wall being at least in part formed by a flexible membrane or the like characterised by features of partitions between two working chambers

Definitions

  • the present invention relates to a liquid filling type vibration damping device.
  • a liquid-filled type vibration damping device is known as a vibration damping device that supports an automobile engine and does not transmit the engine vibration to a vehicle body frame.
  • a liquid-filled type vibration damping device is configured such that a first mounting member mounted on the engine side and a second mounting member mounted on the vehicle body frame side are connected by a vibration-isolating base made of a rubber-like elastic body.
  • a liquid filling chamber is formed between the diaphragm attached to the fixture and the vibration isolating base.
  • the liquid filling chamber is divided into a main liquid chamber and a sub liquid chamber by a partition, and the main liquid chamber and the sub liquid chamber are connected to each other by an orifice.
  • a vibration damping function and a vibration insulating function can be achieved by the fluid flow effect between the two liquid chambers by the orifice and the vibration damping effect of the vibration damping base.
  • the dynamic characteristics based on the fluid flow effect are based on the shape and dimensions (cross-sectional area and length) of the orifice that serves as a passage when the fluid flows, or the characteristics of the fluid (density and viscosity, etc.). Change.
  • the above dynamic characteristics greatly depend on input vibration conditions, especially input amplitude (so-called amplitude dependency).
  • Fig. 13 is a diagram showing the amplitude dependence of the dynamic characteristics of the conventional liquid-filled type vibration damping device.
  • the broken line indicates the dynamic characteristics when a small amplitude (for example, ⁇ 0.1 mm) is input.
  • the solid lines show the dynamic characteristics when a large amplitude (for example, ⁇ lmm) is input.
  • the dynamic characteristics tend to increase the peak value of the mouth factor I as the input amplitude decreases.
  • the amount of change (gradient) of the storage spring constant K d increases, and the value of the storage spring constant K d tends to increase in the frequency region past the peak of the loss factor I.
  • idle vibration generally in the frequency range of 20 Hz to 40 Hz
  • engine shake vibration and blanking vibration Input generally in the frequency range of 10 Hz to 20 Hz
  • the amplitude of the idle vibration is smaller than that (generally ⁇ 0.5 mm to soil 2 mm amplitude).
  • the size of the orifice is tuned so that high damping characteristics can be obtained when inputting low-frequency high-amplitude signals such as engine shake vibrations, unnecessarily high-frequency small-amplitude input signals for idle vibrations are used.
  • the dynamic spring characteristic value is significantly increased, which leads to a reduction in vibration isolation performance.
  • tuning is performed to obtain low dynamic spring characteristics with respect to idle vibration, the damping characteristics will significantly decrease in engine shake vibration, etc., and satisfactory vibration isolation performance will not be obtained.
  • the dynamic spring characteristic and the damping characteristic can be switched in two stages, so that, for example, a high damping characteristic can be exhibited in a low frequency region, and a low dynamic spring characteristic can be exhibited in a high frequency region.
  • an operating means, an electromagnet means, a power supply means, a control means, and the like are required, and the operating means needs to be configured to be movable.
  • the reliability and durability of the device were reduced due to an increase in the number of parts and moving parts.
  • it was difficult to accurately control the cross-sectional area of the orifice and it was difficult to achieve stable vibration isolation performance.
  • a liquid filled type vibration damping device comprises a first mounting member, a cylindrical second mounting member, and a connection between the second mounting member and the first mounting member.
  • An anti-vibration base made of a rubber-like elastic body, a diaphragm attached to the second mounting member to form a liquid enclosing chamber between the anti-vibration base and the anti-vibration base,
  • a partition body for partitioning the main liquid chamber on the substrate side and the sub liquid chamber on the diaphragm side; and an orifice for communicating the main liquid chamber and the sub liquid chamber.
  • a liquid-filled type vibration damping device wherein a short-circuit path connecting between two points of the path with a cross-sectional area smaller than the orifice and shorter than the length of the orifice is formed.
  • the partition body is A pair of lattice members, each having an opening and having the remaining part formed in a substantially lattice shape, and an elastic partition film housed between the opposing surfaces of the pair of lattice members and made of a rubber-like elastic body.
  • a liquid-filled type vibration damping device is the liquid-filled type vibration damping device according to the first or second invention, wherein the partition body comprises a tubular member formed by orifice-forming walls projecting in a radial direction; An outer fitting tubular portion fitted externally to one end in the axial direction of the tubular member is provided on the peripheral edge.
  • a cutting plate member wherein at least a part of the orifice forming wall is extended toward one end side in the axial direction of the tubular member.
  • the liquid-filled vibration damping device is the liquid-filled vibration damping device according to the third invention, wherein the orifice forming wall is provided with two orifices at one end and the other end in the axial direction of the cylindrical member.
  • An orifice intermediate wall having a notch for communicating the two flow paths, and extending from one side of the notch of the orifice intermediate wall toward one axial end of the cylindrical member.
  • a first vertical wall provided, and a second vertical wall extending from the other side of the cutout portion of the orifice intermediate wall toward the other axial end of the cylindrical member.
  • the length of the flow path is substantially one or more turns along the outer circumference of the cylindrical member, and the outer fitting cylindrical portion of the partition plate member is externally fitted to one axial end of the cylindrical member.
  • a gap is formed between the outer fitting tube portion of the partition plate member and the first vertical wall; And it is configured such that the short-circuit path is formed by gap.
  • a pinching member is disposed on the other end side of the tubular member, and the outer diameter of the other end of the tubular member is smaller than the outer diameter of the sandwiching member.
  • a projecting portion projecting from the other end of the cylindrical member may be formed, and the projecting portion may be configured to also serve as an orifice forming wall.
  • the cross-sectional area of the orifice can be prevented from being reduced as compared with the conventional liquid filled type vibration damping device, and the length can be increased without reducing the cross-sectional area.
  • a sufficient fluid damping function can be obtained by securing the fluid flow effect of the orifice.
  • the fitting tubular portion of the pinching member may be configured to be fitted inside the inner peripheral portion on the other end side of the tubular member. This makes it possible to firmly fix the pinching member to the cylindrical member and prevent the displacement thereof.
  • the cylindrical member is formed in a substantially cylindrical shape, and the pair of lattice members is one of the lattice members.
  • the other grid member is provided integrally with the partition plate member, and the other grid member is provided integrally with the partition member at the one axial side of the cylindrical member.
  • a liquid filled vibration isolator according to a sixth invention is the liquid filled vibration isolator according to any one of the first to fifth inventions, wherein the sectional area of the orifice is 1,
  • the piston has an effective area of about 48 to about 72, and the effective area of the piston of the vibration isolating base is about 360 to about 360.
  • a liquid-filled type vibration damping device is the liquid-filled type vibration damping device according to the sixth aspect of the present invention, wherein, when the partition body has the elastic partition film and a grid member, However, if the cross-sectional area of the short-circuit path is 1, the range is from about 900 to about 130.
  • the liquid-filled type vibration damping device is the liquid-filled type vibration damping device according to the fourth aspect of the present invention, wherein a gap between an end of the outer fitting cylinder and an end of the vertical wall includes The length in the axial direction is in the range of about 0.5 mm or more and about 1 mm or less.
  • FIG. 1 is a cross-sectional view of a liquid filling type vibration damping device according to one embodiment of the present invention.
  • FIG. 2A is a top view of the orifice fitting
  • FIG. 2B is a cross-sectional view of the orifice fitting taken along the line I Ib—I Ib in FIG. 2A.
  • FIG. 3 is a side view of the orifice fitting.
  • FIG. 4 (a) is a top view of the partition plate member
  • FIG. 4 (b) is a cross-sectional view of the partition plate member taken along the line IVb-IVb in FIG. 4 (a).
  • FIG. 5 (a) is a top view of the elastic partition film
  • FIG. 5 (b) is a cross-sectional view of the elastic partition film taken along line Vb-Vb in FIG. 5 (a).
  • FIG. 6 (a) is a top view of the holding member
  • FIG. 6 (b) is a cross-sectional view of the holding member taken along the line VIb-VIb in FIG. 6 (a).
  • FIG. 7 (a) is a top view of the partition body and the holding member
  • FIG. 7 (b) is a top view of FIG.
  • FIG. 8A is a cross-sectional view of the partition body and the holding member taken along the line VIIb-VIIb in FIG. 8A.
  • FIG. 8 is a developed schematic view in which the outer peripheral surface of the partition body (orifice fitting) is developed in a plane. .
  • FIG. 9 is a schematic diagram schematically showing a mechanical model of the liquid-filled type vibration damping device.
  • FIG. 10 is a diagram showing dynamic characteristics of the liquid-filled type vibration damping device.
  • FIG. 11 is a view showing a modification of the partition member.
  • FIG. 12 is a view showing a modification of the orifice fitting.
  • FIG. 13 is a diagram showing dynamic characteristics of a conventional liquid-filled type vibration damping device. Explanation of symbols
  • FIG. 1 is a cross-sectional view of a liquid filling type vibration damping device 100 according to an embodiment of the present invention.
  • the liquid filling type vibration damping device 100 supports and fixes an engine of an automobile while maintaining the engine. This is a vibration isolator to prevent vibration from being transmitted to the vehicle body frame.
  • a first mounting bracket 1 attached to the engine side and a cylindrical mounting member attached to the vehicle body frame side below the engine It mainly comprises a second mounting bracket 2 and a vibration-proof base 3 which connects these components and is made of a rubber-like elastic body.
  • the first mounting bracket 1 is formed in a substantially flat shape from a steel material or the like, and as shown in FIG. 1, a mounting port 4 is protruded upward at a substantially central portion thereof.
  • a positioning pin 5 for positioning a stabilizer bracket 8 described later protrudes from a side of the mounting bolt 4.
  • the second brazing metal fitting 2 includes a cylindrical metal fitting 6 on which the vibration-proof base 3 is vulcanized and formed, 4 006399 and a bottom fitting 7 attached below the fitting 6.
  • the cylindrical metal member 6 is formed in a cylindrical shape having an opening extending upward
  • the bottom metal member 7 is formed in a cup shape, each of which is made of a steel material or the like.
  • a mounting port 4 is protruded, and a positioning convex portion 7a is press-formed in a convex shape.
  • the vibration-isolating substrate 3 is formed from a rubber-like elastic body into a substantially truncated conical cross section, and is vulcanized between the lower surface of the first mounting member 1 and the upper end opening of the cylindrical metal member 6. Glued.
  • a rubber film 3 a covering the inner peripheral surface of the cylindrical metal fitting 6 is connected to the lower end of the vibration-proof base 3.
  • the rubber film 3 a is connected to an orifice intermediate wall of an orifice metal fitting 16 described later. 22, the first and second vertical walls 23 a, 23 b, and the outer fitting tube portion 31 of the partition member 17 are in close contact with each other.
  • a protrusion 3 b is formed at one end (right side in FIG. 1) of the vibration-proof base 3, and when the protrusion 3 b comes into contact with the stabilizer bracket 8, a large displacement occurs. It is configured so as to obtain the stopper effect of (1). Note that a part of the cylindrical metal fitting 6 is buried in the protruding portion 3b in order to secure its rigidity.
  • the diaphragm 9 is formed in a rubber film shape having a partially spherical shape from a rubber-like elastic body. As shown in FIG. 1, the diaphragm 9 is attached to the second mounting member 2 (between the cylindrical metal member 6 and the bottom metal member 7). Has been attached. As a result, a liquid filling chamber 11 is formed between the upper surface side of the diaphragm 9 and the lower surface side of the vibration isolating base 3.
  • an antifreeze liquid such as ethylene glycol is sealed in the liquid sealing chamber 11.
  • the liquid filling chamber 11 is divided into a main liquid chamber 11 A on the vibration isolating base 3 side (upper side in FIG. 1) and a diaphragm 9 side (lower side in FIG. 1) by a partition body 12 described later.
  • Sub-chamber 1 1 B is divided into a main liquid chamber 11 A on the vibration isolating base 3 side (upper side in FIG. 1) and a diaphragm 9 side (lower side in FIG. 1) by a partition body 12 described later.
  • the diaphragm 9 is vulcanized and adhered to a donut-shaped mounting plate 10 as viewed from above, and as shown in FIG. 1, the mounting plate 10 is swaged between the cylindrical fitting 6 and the bottom fitting 7. By being fixed, it is attached to the second mounting bracket 2.
  • the partitioning body 12 includes an elastic partitioning membrane 15 formed of a rubber-like elastic body into a substantially disc-shaped rubber film, and an inner peripheral surface that accommodates the elastic partitioning membrane 15.
  • Orifice fitting 16 received by the side wall 16a of this side and this orifice fitting 16 And a disk-shaped partition plate member 17 that covers the opening at one axial end (the upper side in FIG. 1).
  • the partition plate member 17 includes a lattice-shaped wall portion 17a as described later.
  • the elastic partition film 15 is accommodated between opposing surfaces of the wall portion 17a of the partition plate member 17 and the wall portion 16a of the orifice fitting 16, and its displacement is regulated from both sides. Due to this displacement regulation, at the time of large-amplitude input, the film stiffness can be increased to improve the damping characteristics.
  • the elastic partition membrane 15 is stored with a slight gap between it and the walls 16a, 17a, etc., and when a small amplitude is input, the liquid is filled through the gap.
  • the liquid in chamber 11 leaks from main liquid chamber 11A to sub liquid chamber 11B (or vice versa). Due to this leak, it is possible to reduce the dynamic spring when a small amplitude is input.
  • the liquid-filled type vibration damping device 100 of the present embodiment when a relatively small amplitude is input, the liquid pressure difference between the main and sub liquid chambers 11 A and 11 B is reduced. Therefore, when the amplitude is relatively large, the amount of displacement of the elastic partition membrane 15 is restricted from both sides while suppressing the fluid flow effect, thereby increasing the membrane rigidity and ensuring the fluid flow effect. As a result, the dependence of the dynamic characteristics on the amplitude can be effectively reduced in combination with the operation of the short-circuit path s C described later.
  • an orifice 25 is formed between the outer peripheral surface of the orifice bracket 16 and the rubber film 3a that covers the inner peripheral surface of the second mounting bracket 2 (the cylindrical bracket 6). ing.
  • the orifice 25 is an orifice flow path that connects the main liquid chamber 11A and the sub liquid chamber 11B.
  • FIG. 1 illustrates a cross-sectional shape including the axis O (see FIG. 2) of the orifice fitting 16 (that is, a shape obtained by cutting the liquid filled vibration isolator 100 on a plane including the axis O). . Therefore, each area of the substantially rectangular region (three force points in FIG. 1) indicated by reference numeral 25 (R 1) or reference numeral 25 (R 2) in FIG. 1 represents the sectional area of the orifice 25, respectively. This cross-sectional area corresponds to the “cross-sectional area of the orifice” described in claims 1 or 6.
  • the orifice 25 is defined by the orifice intermediate wall 22 as described later. It has two upper and lower orifice flow paths R 1 and R 2 (see FIG. 3), and the cross-sectional area of each of these orifice flow paths R 1 and R 2 is substantially the same. Therefore, the cross-sectional area of the orifice 25 is substantially constant along the flow path direction.
  • the area indicated by the reference numeral 25 (R 1) is the outer peripheral surface of the orifice bracket 16, the inner peripheral surface of the rubber film 3 a, and the upper surface of the orifice intermediate wall 22 (the upper surface in FIG. 1). ) And the lower surface (lower side surface in FIG. 1) of the fitting wall 21 and the outer fitting cylindrical portion 31.
  • the area indicated by the reference numeral 25 (R 2) is the outer peripheral surface of the orifice fitting 16, the inner peripheral surface of the rubber film 3 a, and the lower surface of the orifice intermediate wall 22 (FIG. 1 lower surface).
  • a short-circuit path S C connecting between two points of the path is formed, and is configured so that the amplitude dependence of dynamic characteristics can be reduced.
  • the detailed configuration of the short-circuit path s C will be described later.
  • the area of the region indicated by the symbol SC in FIG. 1 represents the cross-sectional area of the short-circuit path SC, and this cross-sectional area is described in claim 1 or claim 6 or claim 7.
  • Cross-sectional area of short-circuit path ”.
  • the scale of the short-circuit path SC is shown in a state larger than the actual scale for easy understanding.
  • the partition body 12 is moved in the axial direction (FIG. 1 vertical direction) of the second mounting bracket 2 by the partition body receiving portion 3 c provided on the vibration isolating base 3 and the holding member 18. It is pinched and fixed.
  • a second cylindrical portion 44 which will be described later, is press-fitted into the inner peripheral portion of the other end of the orifice bracket 16 in the axial direction (the lower side in FIG. 1), and the outer peripheral side flat plate portion 4 1 Are caulked and fixed to the second mounting bracket 2 (the cylindrical bracket 6 and the bottom bracket 7).
  • the partition body receiving portion 3c is formed as a step extending over the entire circumference on the lower surface side of the vibration isolation base 3, and as shown in FIG. 1, the upper end surface of the partition 12 is locked at the step. I do.
  • the partition receiving portion 3c is compressed and deformed, and the elastic restoring force of the partition receiving portion 3c acts on the partition 12 as a holding force. ing.
  • the partition body 12 can be firmly and stably held and fixed.
  • the second cylindrical portion 44 of the holding member 18 is press-fitted into the inner peripheral portion of the lower end side of the orifice fitting 16 and the outer flat plate portion 4 of the holding member 18 is fitted.
  • the holding member 18 and the partition body 12 can be firmly held. As a result, even if a large amplitude or a high frequency amplitude is input, the chatter of each member can be suppressed, thereby avoiding the influence on the dynamic characteristics due to the displacement or resonance of each member. be able to.
  • FIG. 2 (a) is a top view of the orifice fitting 16 and FIG. 2 (b) is a cross-sectional view of the orifice fitting 16 taken along the line II-IB in FIG. 2 (a).
  • FIG. 3 is a side view of the orifice fitting 16.
  • the orifice fitting 16 has, as shown in FIGS. 2 and 3, an axial core O made of a metal material such as aluminum-palladium, and an inner peripheral side formed in a substantially cylindrical shape having a hollow inside. ing.
  • a fitting wall 21 is provided on the outer periphery of one end of the orifice fitting 16 in the axial direction (for example, the upper side in FIG. 2B or FIG. 3) in the radial direction (axial center). It refers to a direction substantially orthogonal to O.
  • it is formed so as to protrude (ie, protrude outward from the outer peripheral surface of the orifice fitting 16) as shown in FIG.
  • the outer fitting tube portion 31 of the partition plate member 17 is externally fitted into the fitting wall 21 by press fitting (see FIG. 1).
  • a notch 21a is formed in a part of the fitting wall 21 in the circumferential direction, and the notch 21a and a partition plate described later are formed.
  • One end of the orifice 25 (orifice flow path R 1) communicates with the main liquid chamber 11 A (see FIG. 1) via the opening 32 of the member 17 (see FIG. 4).
  • the middle part in the axial direction of the orifice bracket 16 (more precisely, the middle between the lower surface of the fitting wall 21 (Fig. 2b lower side) and the other end surface of the orifice bracket 16 (Fig. 2 (b) lower surface)
  • the orifice intermediate wall 22 extends in the radial direction (refers to the direction substantially perpendicular to the axis O.
  • the orifice bracket 16 is formed to protrude outward from the outer peripheral surface of the orifice bracket 16).
  • the orifice 25 is divided by the orifice intermediate wall 22 so that the orifice 25 has an orifice flow path R 1 for approximately one turn on the upper side (one axial end of the orifice fitting 16) and a lower (orifice fitting 16). (The other end in the axial direction of the orifice) An orifice flow path R2 for approximately one round is formed. As described later, the orifice flow path R2 has a part of the orifice forming wall formed by a sandwiching member 18 (intermediate side flat plate portion 43) (see FIG. 1).
  • the orifice intermediate wall 22 is notched at a part in the circumferential direction, and the rain end of the notch (that is, the orifice intermediate wall 22 in the circumferential direction) is cut out.
  • the first and second vertical walls 23a, 23b extending in the direction of the axis O of the orifice bracket 16 (for example, the vertical direction in FIG. 3) are connected to one end and the other end.
  • first and second vertical walls 23a and 23b project in the radial direction of the orifice bracket 16 (a direction substantially perpendicular to the axis O. For example, in the horizontal direction in FIG. 2 (b)). That is, while being formed outwardly from the outer peripheral surface of the orifice fitting 16), as shown in FIG. 3, the first vertical wall 23 a extends to the fitting wall 21, and the second vertical wall 23 a The wall 23 b extends to the lower end surface of the orifice fitting 16.
  • a course changing portion of the orifice flow paths Rl and R2 is formed between the first and second vertical walls 23a and 23b (see Fig. 9).
  • the orifice 25 having a flow path length of substantially one or more rounds along the outer circumference is provided on the outer circumferential side of the orifice bracket 16. Can be formed. Therefore, a sufficient vibration damping function can be obtained by increasing the length of the orifice 25 and securing the fluid flow effect.
  • the length of the flow path can be changed from approximately one turn to slightly less than two turns by changing the press-fitting position of the holding member 18 and adjusting the circumferential position of the opening 46.
  • the length can be set to an arbitrary length between them (in this embodiment, between about 5Z 8 laps and about 13 to 8 laps).
  • the middle flat plate portion 43 of the sandwiching member 18 is configured to also serve as the orifice forming wall (see FIG. 1), the overall height of the liquid-filled vibration isolator 100 is the same. If this is the case, the flow path of the orifice 25 The area can be prevented from being reduced, and the length of the flow path can be increased without reducing the cross-sectional area of the flow path.
  • a concave notch 24 whose protrusion in the radial direction is reduced, and this concave notch 24 is formed. It is connected to the fitting wall 21.
  • the recess 24 has a radially extending height substantially equal to that of the fitting wall 21, and is substantially flush with the outer peripheral surface of the fitting wall 21.
  • a wall 16a is formed in a body on the inner peripheral side of the orifice bracket 16, and the wall 16a has a plurality of openings (center side).
  • the grid holes 24a and the grid holes 24b, 24c) arranged in two rows in the circumferential direction of the wall 16a are formed in the thickness direction.
  • the wall portion 16a is formed in a substantially lattice shape.
  • the shape of the grid holes 24 a is substantially circular concentric with the axis O of the orifice bracket 16, and the shape of the grid holes 24 b and 24 c Are formed in a shape obtained by radially dividing annular holes along the circumferential direction.
  • the four grid holes 24 b and the eight grid holes 24 c are arranged at substantially equal intervals (approximately 90 degrees or approximately 45 degrees) in the circumferential direction.
  • the grid holes 24b of the outer row are arranged so that the positions in the circumferential direction coincide with the grid holes 24c of the outer row every 45 degrees.
  • FIG. 4 (a) is a top view of the partition plate member 17, and FIG. 4 (b) is a cross-sectional view of the partition plate member 17 taken along the line IVb-IVb in FIG. 4 (a).
  • the partition plate member 17 is formed in a substantially disc shape having an axis P from a steel material or the like.
  • a plurality of openings are provided on the inner peripheral side (plate surface) of the partition member 17, a plurality of openings (grid holes 34b and 34c arranged in two rows in the circumferential direction and the grid holes 34a on the center side) are provided. In this direction, thereby forming a substantially lattice-shaped wall portion 17a integrally.
  • the wall 17a and the lattice holes 34a to 34c have the same pattern (position, size) as the wall 16a and the lattice holes 24a to 24c of the orifice bracket 16 described above. , Range, etc.), and a description thereof will be omitted.
  • an outer fitting cylindrical portion 31 is provided on the outer peripheral portion of the partition plate member 17 at substantially the same height (vertical height in FIG. 4 (b)) over the entire circumference. ing.
  • the partition member 17 is formed by externally fitting the outer fitting cylindrical portion 31 to the outer periphery of the above-mentioned one end of the orifice fitting 16 in the axial direction, that is, to the fitting wall 21 of the orifice fitting 16. Assembled to bracket 16.
  • the outer fitting cylinder 31 has a lower end surface (FIG. 4 (b) lower surface) having an end surface portion 23 a of the first vertical wall 23 a of the orifice bracket 16 (FIG. 2). (See Fig. 3 or Fig. 7).
  • the lower end face of the outer fitting tube 31 and the first vertical wall 23a (the end face 2 Between 3a1), a gap is formed as a short-circuit path SC (see Fig. 1 or Fig. 7).
  • an opening 32 is formed in the wall portion 17a of the partition member 17 outside the lattice hole 34c in the plate thickness direction. As described above, the opening 32 is formed with the orifice 25 (orifice flow path R 1) through the notch 21 a of the orifice fitting 16 (see FIGS. 2 and 3). An opening that communicates with 11 A.
  • the opening 32 is formed in a substantially elliptical shape curved along the circumferential direction.
  • the opening 32 is set so that its circumferential length is longer than the notch 21a of the orifice bracket 16 (see FIG. 7). Therefore, when the partition plate member 17 is assembled to the orifice fitting 16, it is possible to prevent the cross-sectional area of the orifice 25 from decreasing even if the assembly position is slightly shifted in the circumferential direction.
  • FIG. 5 (a) is a top view of the elastic partition membrane 15 and FIG. 5 (b) is a cross-sectional view of the elastic partition membrane 15 taken along line Vb-Vb in FIG. 5 (a).
  • Figure 5 ( In 9a) the groups of ribs (annular and radial ribs 15a, 15b) are shown using dashed-dotted lines to simplify the drawing and facilitate understanding.
  • the elastic partition membrane 15 is housed in the partition body 12 (between the opposing surfaces of the wall portion 16a of the orifice fitting 16 and the wall portion 17a of the partition member 17). It functions to reduce the hydraulic pressure difference between the main and sub liquid chambers 11A and 11B, and is formed in a substantially disc shape from a rubber-like elastic material. As shown in FIG. 5, rib groups project from both upper and lower surfaces of the elastic partition film 15. In addition, the pattern of the rib group on the upper surface side is formed the same as the pattern of the rib group on the lower surface side.
  • the rib group includes an annular rib 15a configured as an annular ridge and a radial rib 15b configured as a radial ridge.
  • the height of the annular rib 15a is set so that the top is located away from the walls 16a and 17a when the partition 12 is assembled.
  • the height of the radial ribs 15b is set so that the tops thereof come into contact with the walls 16a and 17a in the assembled state of the partition body 12, and the radial ribs 15b Is also set to a small rib width.
  • FIG. 6 (a) is a top view of the holding member 18 and FIG. 6 (b) is a cross-sectional view of the holding member 18 along the line VIb-VIb in FIG. 6 (a).
  • the sandwiching member 18 is a member for sandwiching and holding the partition body 12 between the vibration isolating base 3 (see FIG. 1), and as shown in FIG. It is formed in a substantially disk shape.
  • the holding member 18 includes an outer peripheral side flat plate portion 41, a first cylindrical portion 42 that tightly seals the lower end portion of the rubber film 3 a, and a lower end of the orifice fitting 16.
  • first and second cutout portions 45 a and 45 b are formed in the outer peripheral side flat plate portion 41.
  • the first and second cutouts 45 a and 45 b are identification means for identifying the rotational direction position of the holding member 18, and the outer peripheral end of the outer peripheral side flat plate portion 41 is differently cut. It is configured as a notch with a notch.
  • the first and second cutouts 45a, 45b are formed with different cutout shapes, so that the press-fitting reference position (the position of each cutout 45a, 45b) is obtained. ) Can be prevented, and the press-fitting position failure caused by such a work error can be avoided. Further, after the press-fitting operation, the inspection of the press-fitting position failure and the like can be efficiently performed based on the shapes of the notches 45a and 45b.
  • the specific shape of the first and second cutouts 45a and 45b is as shown in FIG. 6 (a).
  • the first notch 45a is composed of two concave notches
  • the second notch 45b is composed of two concave notches.
  • one notch 45a, 45b extends from the other notch 45b, 45a approximately 170 ° along the arc of the outer peripheral side flat plate 41. It is arranged at a place that is separated.
  • the first and second cutouts 45 a and 45 b are formed as cutouts formed by cutting out the outer peripheral end of the holding member 18 (the outer peripheral side flat plate 41).
  • the formation cost can be reduced.
  • the holding member 18 is formed by punching a plate-shaped material into a predetermined outer shape and press-forming the punched material.
  • the first and second cutouts 45 a , 45b are formed as cutouts, so in the process of punching a flat material, the first and second cutouts 45a, 45b are also formed by punching at the same time. be able to. As a result, a separate process is not required for forming the first and second cutouts 45a and 45b, and the molding cost can be reduced accordingly.
  • the identification means when configured as a protruding piece that protrudes in the radial direction from the outer peripheral end of the outer peripheral portion side flat plate portion 41, the holding member 18 is connected to the second mounting member 2 (the cylindrical metal member 6). ) When inserting into the inside, the protruding piece interferes with the lower end (lower end in Fig. 1) of the cylindrical fitting 6, and the insertion workability is hindered. Where there is a problem that the holding member 18 is deviated in the radial direction (see FIG. 1), if the identification means is configured as a cutout portion (first and second cutout portions 45a, 45b), It is possible to avoid problems that workability is impaired and the position of the holding member 18 is deviated in the radial direction.
  • the intermediate side flat plate portion 43 is configured to also serve as an orifice forming wall (see FIG. 1). That is, the above-mentioned orifice fitting 16 has an outer diameter at the lower end portion smaller than the outer diameter size of the middle side flat plate portion 43 (see FIG. 1).
  • the portion 43 also serves as an orifice forming wall of the orifice 25 (orifice flow path R 2) as a projecting portion that projects radially from the lower end of the orifice fitting 16.
  • a substantially elliptical opening 46 extending along the circumferential direction is formed in the middle flat plate portion 43, that is, the orifice forming wall, in the plate thickness direction (FIG. 6 (a)). (Perpendicular to the paper).
  • the orifice 25 (orifice flow path R 2) communicates with the auxiliary liquid chamber 11 B via the opening 46 (see FIG. 1).
  • the outer peripheral portion of the second cylindrical portion 44 has a substantially circular cross section perpendicular to the axis Q, and the other end in the axial direction of the orifice bracket 16 (see FIG. 2 (b)).
  • Fig. 2 (b) (bottom) The inner periphery also has a substantially circular cross section perpendicular to the axis O. Therefore, the holding member 18 can press-fit the second cylindrical portion 44 into the inner peripheral portion on the lower end side of the orifice fitting 16 at an arbitrary press-fitting position (rotational direction position).
  • the second cylindrical portion 44 of the holding member 18 is press-fitted into the inner peripheral portion on the lower end side of the orifice fitting 16, so that the position of the holding member 18 and the orifice fitting 16 is adjusted.
  • the displacement can be prevented. That is, the press-fitting position of the holding member 18 can be firmly maintained by the holding force such as the elastic restoring force or the frictional force of the inner fitting press-fitting portion.
  • the holding force such as the elastic restoring force or the frictional force of the inner fitting press-fitting portion.
  • the second cylindrical portion 44 of the holding member 18 is press-fitted into the inner peripheral portion of the other end in the axial direction of the orifice fitting 16 (for example, the lower side in FIG. 7B).
  • 16 and 18 can be integrated (see Fig. 7 or Fig. 8). Therefore, both the members 12 and 18 can be transported and mounted in the second mounting bracket 2 (cylindrical bracket 6) at one time. In addition, it is possible to reduce the cost of assembling the liquid-sealed vibration isolator 100.
  • FIG. 7A is a top view of the partition body 12 and the holding member 18, and FIG. 7B is a partition body 12 and the holding member 1 along the line VI lb-VII b in FIG. 7A.
  • FIG. 8 is a sectional view of FIG.
  • the arrow X shown in FIG. 7 indicates the press-fit reference position X of the sandwiching member 18 with respect to the partition 12 (orifice fitting 16).
  • the holding member 18 has its outer peripheral side held by a holding tool (not shown) and is pressed into the orifice fitting 16.
  • the holding face of the holding tool has a first or second cutout 45.
  • Positioning projections are provided to engage with a and 45b to position the press-fitting position (rotational direction position) of the holding member 18.
  • the circumferential position of the positioning projection corresponds to the press-fit reference position X.
  • the elastic partition membrane 15 is placed on the wall 16 a of the orifice bracket 16, and then the partition plate member 1 is fitted on the fitting wall 21 of the orifice bracket 16. This is performed by externally fitting the outer fitting cylinder 31 of FIG. As shown in FIG. 7A, the opening 32 of the partition plate member 17 is formed by the notch 2 of the orifice bracket 16. It is placed at the position that matches 1a.
  • the elastic partition membrane 15 When the partition body 12 is assembled, as shown in FIG. 7, the elastic partition membrane 15 is housed between the opposing surfaces of the pair of walls 16a and 17a, and the elastic partition membrane 15 is displaced. The amount is regulated from both sides (Fig. 7 (b) top and bottom). In addition, between the lower end surface of the outer fitting tube portion 31 of the partition member 17 (FIG. 7 (b) lower surface) and the end surface portion 23 a 1 of the first vertical wall 23 a of the orifice bracket 16. A void is formed as a short-circuit path SC (see Fig. 1 or Fig. 8).
  • the liquid-filled type vibration damping device 100 of the present embodiment only by assembling the two members (that is, the orifice fitting 16 and the partition plate member 17), the gap portion as the short-circuit path SC Can be formed. Therefore, there is no need to separately perform machining such as cutting in order to form the short-circuit path s C, and the machining cost can be reduced. As a result, the liquid-filled vibration isolator 100 as a whole can be reduced accordingly. The product cost can be reduced.
  • the partition plate member 17 is removed to one end of the orifice bracket 16. If the first operation of fitting is performed, the first process of forming the short-circuit path SC and the second process of restricting the displacement amount of the elastic partition film 15 from the both sides thereof by the walls 16a and 17a. And can be performed simultaneously. As a result, the work process can be made more efficient, so that the work cost can be reduced and the product cost of the liquid-filled vibration isolator 100 as a whole can be reduced accordingly.
  • the gap between the lower end surface of the outer fitting tube portion 31 (the lower surface of FIG. 7 (b)) and the end surface portion 23a1 of the first vertical wall 23a is an axial shaft.
  • the length in the core direction (the vertical direction in Fig. 7 (b)) was set to be approximately 0.5 mm or more.
  • the length of the gap in the axial direction is approximately 1 mm or less. It was configured as follows. Thereby, when the orifice fitting 16 and the partition plate member 17 are assembled, it is possible to prevent the height of the partition body 12 from becoming too high, and accordingly, the liquid-filled core-proof device 100 The overall size can be reduced.
  • the short-circuit path S C (void) needs to be formed in a predetermined cross-sectional area as described later.
  • the length in the axis direction (height of the short-circuit path SC) is set to approximately lmm or less
  • the width of the short-circuit path ie, the direction perpendicular to the axis
  • Width can be increased. In other words, it is possible to prevent the width of the short-circuit path from becoming extremely small at least.
  • the first vertical wall 23a (concave notch 24) and the external fitting tube 31 can be made relatively unnecessary to perform precise machining, which facilitates processing and dimensional control. Accordingly, it is possible to suppress an increase in processing cost / management cost.
  • the holding member 18 is press-fitted.
  • the first or second notch 45a, 45b is used as a press-fit reference (that is, the first or second notch 45a, 45b is used as the press-fit reference position). X).
  • the press-fitting position accuracy can be improved, and the occurrence of a press-fitting position defect due to a work error or the like can be suppressed.
  • the holding member 18 was press-fitted with reference to the first cutout portion 45a (in accordance with the press-fit reference position X).
  • the opening 46 of the sandwiching member 18 coincides with the position of the opening 32 of the partition member 17, as described later, the flow path length of the orifice 25 is The length is set to approximately one circumference around the axis 6 (see Fig. 8).
  • the opening 46 of the sandwiching member 18 is arranged at a position circumferentially separated from the opening 32 of the partition plate member 17, and the flow path length of the orifice 25 is the longest (approximately 1). 3 ⁇ 8 laps).
  • FIG. 8 is a schematic development view showing the outer peripheral surface of the partition body 12 (orifice fitting 16) developed in a plane, and shows the state shown in FIG. 7 (with the first cutout 45a as a press-fit reference). State).
  • FIG. 8 the illustration of the partition member 17 and the sandwiching member 18 is omitted, and the positions of the openings 32, 46 of the members 17, 18 are imaginary using the two-dot chain line. This is shown schematically.
  • the opening portion 46 of the sandwiching member 18 is partitioned as shown in FIG. It is arranged below the opening 32 of the plate member 17 (that is, at a position substantially coincident with the circumferential direction).
  • the orifice 25 flows from the main liquid chamber 11A to the upper orifice flow path R1 through the opening 32 (notch 21a). While passing through the orifice flow path R1 from the beginning to the end, the course is changed to the lower orifice flow path R2 between the first and second vertical walls 23a and 23b, and the orifice flow path is changed to the lower orifice flow path R2. After passing a predetermined distance through R 2, a path C having a length of about one circumference along the outer periphery of the orifice fitting 16, which flows out to the sub liquid chamber 11 B through the opening 46. It is configured for.
  • the first vertical wall 23 a (end surface portion 23 a 1) of the orifice fitting 16 and the lower end surface of the outer fitting cylindrical portion 31 (not shown) of the partition plate member 17 are formed. A gap is formed between them (see Fig. 1 or Fig. 7).
  • the orifice 25 path As shown in Fig. 8, there is a short circuit between two points on the path (between PI and P2) that is connected by a path smaller than the cross-sectional area of the path C and shorter than the length of the path C. Path SC is formed.
  • the path C includes a first position P 1 immediately after flowing into the upper orifice flow path R 1 from the opening 32 (the notch 21 a), and the first position P 1.
  • a short circuit SC connects the two points with the second position P 2 when changing course to the lower orifice flow path R 2.
  • the width of the first vertical wall 23a is preferably about 15% or less of the outer diameter of the orifice bracket 16 (the inner diameter of the orifice passages R1, R2). More preferably, the width is approximately 10% or less. Short circuit path Make the RC path long enough By shortening the length to avoid functioning as an orifice flow path, the occurrence of liquid column resonance is suppressed and the amplitude dependence of dynamic characteristics is reliably reduced.
  • FIG. 9 is a schematic diagram schematically showing a mechanical model of the liquid-filled type vibration damping device 100.
  • FIG. 10 is a diagram showing dynamic characteristics (storage spring constant K d, loss factor I) of the liquid-filled type vibration damping device 100.
  • Fig. 10 The excitation conditions in Fig. 10 were: preload (weight of engine in Fig. 9): 100 N, input amplitude: 1 mm (dashed line in Fig. 10) and 0.1 mm (Fig. 10). (Solid line in 10).
  • the liquid filled vibration isolator 100 has an orifice 25 (path C) in which a main liquid chamber 11 A of expanded elasticity K 1 and a sub liquid chamber 11 B of expanded elasticity K 2 are connected. Communication.
  • the path C of the orifice 25 is a short-circuit path S having a smaller cross-sectional area between the two points in the path C than the path C and a shorter length than the path C. It is connected by.
  • the elastic partition membrane 15 has a wall having lattice holes 24a to 24c and 34a to 34c. It is housed between 16a and 17a, and is configured to flow and block the flow of fluid between the main and sub liquid chambers 11A and 11B according to the magnitude of the input amplitude. ing.
  • the characteristic elasticity of the elastic substrate 3 (not shown) is represented by using a symbol K.
  • the liquid-filled type vibration damping device 100 when a relatively large amplitude is input, the flow rate of the orifice 25 (path C) is secured, and the fluid flow effect is exhibited, while the relatively small amplitude is applied.
  • the fluid tries to pass through a shorter path (that is, the short-circuit path SC), so that the flow rate of the orifice 25 (path C) is reduced, and the fluid flow effect can be suppressed accordingly.
  • the dynamic characteristics storage spring constant Kd, loss factor I
  • the dynamic characteristics can greatly reduce the dependence on the input amplitude (amplitude dependence).
  • the elastic partitioning membrane 15 is connected to a pair of walls 16a and 17a.
  • the hydraulic pressure difference between the main and sub liquid chambers 11A and 11B is reduced, and the fluid flow effect is suppressed.
  • the amount of displacement of the elastic partition membrane 15 is regulated from both sides by the walls 16a and 17b to increase the membrane rigidity and secure the fluid flow effect. As a result, it is possible to further reduce the dependency of the dynamic characteristic on the amplitude (amplitude dependency), in combination with the above-described operation of the short-circuit path SC.
  • the cross-sectional area of the short-circuit path SC (gap), the cross-sectional area of the orifice 25, the lattice holes 24a to 24c, 34a to 34c of the walls 16a and 17a
  • the effective area of the piston of the vibration-isolating substrate 3 is set to approximately 1 square millimeter, approximately 60 square millimeters, approximately 1100 square millimeters, and approximately 300000 square millimeters, respectively (ie, The ratio of each area is approximately 1: approximately 600: approximately 110: approximately 300000).
  • the fluid flow effect of the orifice 25 can be secured, and the synergistic effect of the short-circuit path SC and the elastic partition film 15 can be more effectively exerted while suppressing the reduction of the damping characteristic. .
  • the amplitude dependence of the dynamic characteristics with respect to the input amplitude in the range of approximately 0.05 mm to approximately 2 mm in the frequency range of approximately 5 Hz to approximately 40 Hz Properties can be effectively reduced.
  • the ratio of the above areas is the target value (center value), meaning that any one area or all areas are within the range of about ⁇ 20% variation. It is. Within the range of the variation, the amplitude dependency can be sufficiently reduced.
  • the distal end portion (lower end surface) of the outer fitting tube portion 31 may be formed in a flat surface shape.
  • the dimensional variation of the air gap formed between the first vertical wall 23a and the end surface portion 23a1 can be further reduced.
  • dynamic characteristics can be exhibited stably.
  • the orifice intermediate wall 22 is formed at a substantially axially intermediate portion of the orifice fitting 16, and the flow path length of the orifice 25 is substantially along the outer circumference of the orifice fitting 16.
  • it is configured to have one or more turns, it is not necessarily limited to this, and it is naturally possible to configure without providing the orifice intermediate wall 22 as shown in FIG.
  • FIG. 12 is a view showing a modified example of the orifice fitting 16
  • FIG. 12 (a) is a side view of the partition 12
  • FIG. 12 (b) is a partition 12 (orifice FIG. 4 is a developed schematic diagram showing the outer peripheral surface of the metal fitting 1 16) developed in a plane.
  • the same parts as those in the above-described embodiment are denoted by the same reference numerals, and description thereof will be omitted.
  • the orifice fitting 1 16 is formed with a vertical wall 123 a extending radially while extending in the axial direction.
  • the orifice 125 has an orifice flow path R3 formed along its outer periphery.
  • a concave notch 24 having a reduced radial protrusion and an end face 23 a 1 are formed at the end of the vertical wall 123 a. .
  • the two points are connected by a path whose cross-sectional area is smaller than that of the path C and shorter than the path C.
  • Short circuit C is formed.
  • a short-circuit path connecting two points of the path is formed in the path of the orifice, and the short-circuit path is smaller than the cross-sectional area of the orifice, and The orifice was configured to be shorter than the length.
  • the liquid-filled type vibration damping device of the present invention unlike the conventional liquid-filled type vibration damping device, there is no need to provide an actuating means or an electromagnet means, or to dispose the actuating means movably. . Therefore, since the structure can be simplified, the cost of parts and assembly can be reduced, and the product cost of the liquid-filled vibration damping device as a whole can be reduced. is there. In addition, by reducing the number of parts and eliminating the need for movable parts, it is possible to improve reliability and durability, and to exhibit stable vibration isolation performance.
  • the partition member is provided between the pair of grid members and the opposing surfaces of the pair of grid members. Since it is configured to include the elastic partition film to be stored, there is an effect that the amplitude dependency can be further reduced.
  • the hydraulic pressure difference between the main and sub liquid chambers is reduced by the elastic partition film to suppress the fluid flow effect
  • the displacement amount of the elastic partition film is reduced.
  • the partition plate member is fitted around one end of the cylindrical member in the axial direction.
  • a gap as a short-circuit path can be formed between a part of the orifice forming wall and the outer fitting cylinder.
  • the cylindrical member in addition to the effect of the liquid-filled type vibration damping device of the third invention, is provided with an orifice intermediate wall and first and second vertical walls. Since the length of the flow path is configured to be substantially one or more rounds along the outer circumference of the cylindrical member, the length of the flow path can be increased. As a result, there is an effect that a sufficient fluid damping function can be obtained by securing the fluid flow effect of the orifice.
  • a pair of lattice members are integrally formed with each of the cylindrical member and the partition plate member.
  • the first step of forming a gap as a short-circuit path in the first operation of externally fitting the partition plate member to one end in the axial direction of the cylindrical member, and the elastic partition film formed by a pair of lattice members And the second step of restricting the amount of displacement from both sides can be performed simultaneously.
  • the cross-sectional area of the short-circuit path, the cross-sectional area of the orifice, and the vibration-proof substrate is approximately 1: approximately 60: approximately 300, so that the fluid flow effect of the orifice is secured, and the dynamic characteristics of the orifice are suppressed while the damping characteristics are not reduced. There is an effect that the dependence of the characteristic on the input amplitude can be effectively reduced.
  • the ratio of the cross-sectional area of the short-circuit path to the cross-sectional area of the opening of the lattice member is approximately 1 : Since it is approximately 110, the fluid flow effect of the orifice is ensured, and the reduction in the damping characteristics is suppressed, while the synergistic effect with the short circuit path can be more effectively exerted. There is. As a result, the dynamic characteristics depend on the input amplitude. It can be further reduced.
  • the end of the outer fitting tube portion and the end of the vertical wall can be provided. Since the length of the cylindrical member in the axial direction is approximately 0.5 mm or more, even when the dimensional variation of the cylindrical member and the partition member overlaps in the axial direction of the cylindrical member, However, there is an effect that the short-circuit path is reliably formed, and the amplitude dependency can be reduced stably. That is, if the length is shorter than about 0.5 mm, the influence of the dimensional variation of each member on the size of the gap (short-circuit path) becomes excessive, and a short-circuit path having an appropriate cross-sectional area cannot be formed.
  • the length of the above-mentioned gap is about 1 mm or less in the axial direction of the cylindrical member, the height of the partition body becomes too high when the cylindrical member and the partition plate member are assembled. This has the effect of reducing the size of the liquid-filled core protection device as a whole.
  • the short-circuit path it is necessary to set the cross-sectional area of the short-circuit path to a predetermined size. If the above-mentioned length (the height of the short-circuit path) is set to approximately 1 mm or less, the short-circuit is proportionally increased. Since the width of the path (that is, the width in the direction perpendicular to the axis of the cylindrical member) can be increased, it is possible to suppress an increase in costs such as processing in the width direction of the short-circuit path and dimensional control. effective. That is, when the above-mentioned length (height of the short-circuit path) exceeds l mm, the width of the short-circuit path becomes too small, and it becomes difficult to process and dimensionally control the short-circuit path.

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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

Dispositif isolateur de vibrations à liquide scellé capable de réduire la dépendance des caractéristiques dynamiques vis-à-vis de la grandeur d’une amplitude d’entrée, dans lequel un orifice (25) est formé d’un chemin (C) comportant des passages d’écoulement à orifice (R1) et (R2). Un chemin de court-circuitage (SC) présentant une section transversale inférieure à celle du chemin (C) et une longueur inférieure à celle du chemin (C) reliant deux points du chemin (C) est formé dans le chemin (C) de l’orifice (25). Comme le fluide a tendance à emprunter le chemin le plus court (autrement dit, le chemin de court-circuitage SC) lorsqu’une amplitude relativement faible est appliquée à l’entrée, il est possible de réduire la quantité d’écoulement dans l’orifice (25) (chemin C) de façon à supprimer ainsi l’effet de l’écoulement du fluide. Il est donc possible de réduire la dépendance des caractéristiques dynamiques vis-à-vis de l’amplitude d’entrée.
PCT/JP2004/006399 2004-04-30 2004-04-30 Dispositif isolateur de vibrations a liquide scelle WO2005106283A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/JP2004/006399 WO2005106283A1 (fr) 2004-04-30 2004-04-30 Dispositif isolateur de vibrations a liquide scelle
JP2006516829A JP4212624B2 (ja) 2004-04-30 2004-04-30 液封入式防振装置

Applications Claiming Priority (1)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114402148A (zh) * 2019-09-17 2022-04-26 株式会社普利司通 隔振装置
EP4227552A4 (fr) * 2020-10-08 2024-10-23 Prospira Corp Dispositif d'isolation de vibrations

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04203631A (ja) * 1990-11-30 1992-07-24 Tokai Rubber Ind Ltd 流体封入式マウント装置
JP2004019704A (ja) * 2002-06-13 2004-01-22 Toyo Tire & Rubber Co Ltd 液封入式防振装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04203631A (ja) * 1990-11-30 1992-07-24 Tokai Rubber Ind Ltd 流体封入式マウント装置
JP2004019704A (ja) * 2002-06-13 2004-01-22 Toyo Tire & Rubber Co Ltd 液封入式防振装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114402148A (zh) * 2019-09-17 2022-04-26 株式会社普利司通 隔振装置
EP4227552A4 (fr) * 2020-10-08 2024-10-23 Prospira Corp Dispositif d'isolation de vibrations

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JP4212624B2 (ja) 2009-01-21
JPWO2005106283A1 (ja) 2007-12-13

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