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
  • F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
  • F16F13/1463—Units of the bushing type, i.e. loaded predominantly radially characterised by features of passages between working chambers

Definitions

• the present invention relates to a fluid-filled cylindrical mount device that obtains a predetermined vibration-proofing effect based on the flow of a fluid sealed therein, and in particular, the improvement of the vibration-proofing effect based on the flow of the fluid.
• the present invention relates to a fluid-filled cylindrical mounting device which can be advantageously provided with a simple structure.
• an inner cylindrical fitting and an outer cylindrical fitting arranged at a predetermined distance in a radial direction are used as a type of a mounting device that is interposed between members constituting a vibration transmission system and vibration-isolated and connected to each other.
• an inner cylindrical fitting and an outer cylindrical fitting arranged at a predetermined distance in a radial direction are used as a type of a mounting device that is interposed between members constituting a vibration transmission system and vibration-isolated and connected to each other.
• a rubber elastic body interposed between them, so as to attenuate or cut off vibration input mainly in a predetermined direction.
• Mounting devices are known. For example, a suspension bush of a car or a cylindrical engine mount.
• the frequency at which the vibration damping effect due to the resonance action of the fluid that is swirled in the orifice passage can be exhibited is as follows. Tuning is performed by the ratio (a / £) of the flow cross-sectional area (a) of the orifice passage and its length (: ⁇ ), and the vibration isolation effect due to the resonance action of the fluid. Can be more effectively exerted as the cross-sectional area (a) of the five office passages is larger.
• the orifice passage is formed in such a way that it penetrates through the fluid chambers and penetrates the rubber elastic body and extends straight, the flow path length is short, and therefore, especially in the low frequency range. Large cross-sectional distribution when tuning to The problem was that the orifice passage could not provide a sufficient vibration damping effect because it could not be set properly.
• the outer peripheral metal fitting has a cylindrical shape as a whole on the inner peripheral surface.
• An orifice metal fitting is provided, and an orifice passage extending in the circumferential direction is formed between the orifice metal fitting and the outer cylindrical metal fitting, so that the length of the orifice is one or more rounds in the circumferential direction of the mount.
• An orifice passage has been proposed that allows the formation of an orifice passage that has a flow cross-section that can be advantageously ensured even when tuning to a lower frequency range.
• the present invention has been made in view of the above circumstances, and the problem to be solved is that the flow path length of the orifice passage is limited to a special member. Orifice, which can be advantageously secured with a simple structure without adding heat, and which can exert an excellent vibration-damping effect based on the resonance action of the fluid flowing inside the orifice. It is an object of the present invention to provide a fluid-filled cylindrical mounting device having a mechanism.
• the present invention (A) an inner cylinder fitting; (b) a medium-sleeved sleeve having a plurality of windows concentrically or eccentrically arranged outside the inner cylinder fitting; An outer cylinder fitting detached and mounted on the peripheral surface of the simple sleeve, and (d) interposed between the inner cylinder fitting and the middle sleeve to integrally connect them. ( E ) a rubber elastic body comprising: a socket portion that opens to the outer peripheral surface through a window portion provided in the intermediate sleeve on a radially opposite side of the inner cylindrical metal member.
• the rubber elastic body is formed with a seal rubber which is pressed against In the window portion of the simple sleeve, a relative internal pressure fluctuation is generated at the time of vibration input between the inner and outer cylindrical fittings, which is formed by 'closed in a fluid-tight manner by the cylindrical fittings'.
• the gist of the present invention is a canister-filled cylindrical mount device having a plurality of fluid chambers that are mutually different and an orifice passage that allows the flow of the sealed fluid in the fluid chambers. is there.
• the flow having the structure according to the present invention is as follows.
• the body-mounting type cylindrical mounting device it is interposed between the fitting surface of the inner sleeve and the outer tube fitting, which has been conventionally used to ensure the sealing performance of the sealed fluid.
• an orifice is formed by the seal rubber, so that a special member is not required for forming the orily, and Since the shape of the concave groove can be arbitrarily set at the time of molding the seal rubber, a meandering orifice passage having a long flow path length can be easily formed.
• the flow path length of the orifice path can be advantageously ensured, the flow path area can be set sufficiently large even when tuning to a low frequency range. Therefore, a fluid-filled cylindrical mounting device having excellent vibration damping characteristics can be provided at low cost and with good manufacturability.
• the rubber seal is formed by rotating the rubber elastic body to the outer peripheral surface of the intermediate sleeve. It is formed integrally with the body.
• the seal rubber is formed separately from the rubber elastic body. Further, in an advantageous specific example of the fluid-filled cylindrical mounting device as described above, the seal rubber is formed with a thickness of 1.5 or more. Further, in another advantageous specific example of the fluid-filled cylindrical mounting device as described above, a concave groove provided in the seal rubber extends circumferentially between the windows of the center sleeve. ⁇ 1.5 It is formed in a meandering form that reciprocates 5 times.
• the concave portion protrudes from the bottom surface of the curved portion, and A guide plate is formed to extend in the widthwise middle portion of the groove in the longitudinal direction of the flow path.
• the plurality of fluid chambers are located in a rainfall direction in the ⁇ direction with the inner cylindrical fitting interposed therebetween.
• the orifice passages are formed in a pair of fluid chambers, and the orifice passages are formed in both inversion directions of the respective fluid chambers.
• the plurality of ⁇ fluid chambers are located in a radial direction with the inner cylindrical fitting interposed therebetween, and It is composed of a pair of pressure receiving chambers in which the vibrations input to the inner and outer cylinder fittings are applied to cause internal pressure fluctuations in which the positive and negative directions are opposite to each other.
• the plurality of fluid chambers are located on both radial sides of the inner cylindrical metal fitting.
• the plurality of fluid chambers are located on both sides in the ⁇ direction with respect to the inner cylindrical metal fitting.
• the orifice passage is formed in such a manner that the orifice passage is formed so as to straddle the balance chamber and the pressure receiving chamber while being constituted by one or more balance chambers.
• the vibration inputted between the inner and outer cylindrical fittings of the plurality of fluid chambers is applied.
• An annular restraining member is buried and arranged in the rubber elastic body constituting the peripheral wall of the fluid chamber configured so as to cause internal pressure fluctuation to surround the fluid chamber.
• the rubber elastic body In the portion where the fluid chamber is not formed in the above, a void penetrating in the axial direction is formed.
• the fluid chamber faces outward in the radial direction where the fluid chamber is located.
• a protruding portion is formed on a protruding end face of the protruding end face, the protruding end portion being opposed to the outer cylindrical metal member by a predetermined distance.
• the flange portion has a rectangular cylindrical shape
• the inner cylindrical metal fitting has a rectangular shape. It is composed of a collar that is externally attached and attached.
• the mounting part is provided such that the outer cylindrical fitting is mounted to one member to be vibration-isolated. It is configured as a bracket that integrally has
• the intermediate sleeve and the outer sleeve are each formed by a cylindrical pull-out. They are arranged in a potable manner.
• the intermediate sleeve and the outer cylindrical metal fitting are each a rectangular cylindrical shape. And are arranged simultaneously with each other.
• FIG. 1 is a cross-sectional view showing a specific example of an engine mount having a structure according to the present invention.
• FIG. 2 is a cross-sectional view of FIG.
• FIG. 3 is a sectional view taken along the line DI-DI in FIG.
• FIG. 4 is a cross-sectional view showing an integrally vulcanized molded product constituting the engine mount shown in FIG.
• FIG. 5 is a sectional view taken along line VV in FIG.
• FIG. 6 is a view taken in the direction of arrow a in FIG.
• FIG. 7 is a cross-sectional view showing an engine mount as another embodiment of the present invention.
• FIG. 8 is a sectional view taken along the line VI-VDI in FIG.
• FIG. 9 is a sectional view taken along the line K-K in FIG.
• FIGS. 1 to 3 show a specific example in which the present invention is applied to an automobile engine mount.
• reference numeral 10 denotes an inner cylindrical fitting, on the outer side of which a metal sleeve 12 is arranged eccentrically by a predetermined distance, and integrally formed by a rubber elastic body 14 interposed between the sleeves.
• the outer sleeve of the metal sleeve 12 is further provided with an outer tube fitting 16 on the outer peripheral surface thereof.
• the inner cylinder fitting 10 and the outer cylinder fitting 16 are attached to one of the power unit side and the power unit that holds the engine to prevent the power unit from being attached to the vehicle body. It is designed to support them.
• the inner cylinder fitting 10 is formed in a cylindrical shape, and has an outer peripheral surface at a central portion in the ⁇ direction.
• a brim-shaped cylindrical body-shaped metal fitting 18 is externally fixed.
• the inner cylinder fitting 10 is mounted on the vehicle body or on the power cut side through a port ′ or the like which is inserted and fixed in the inner hole. It is.
• a metal sleeve 12 having a thin-walled P5 cylindrical shape is disposed outside of the inner cylindrical metal fitting 10 in the ⁇ direction in such a manner that the metal sleeve 12 is located at a predetermined distance in the acicular direction.
• a rubber elastic body 14 is interposed 5 between the inner cylindrical fitting 10 and the metal sleeve 12, and the rubber elastic body is provided.
• 14 is the outer peripheral surface of the inner cylinder fitting 10 It is formed as an integral vulcanized molded product 20 which is respectively vulcanized and bonded to the inner peripheral surface of the metal sleeve 12.
• the metal sleeve 12 constitutes an intermediate sleeve.
• the rubber elastic body 14 is exposed up to the outer peripheral surface of the metal sleeve 12 and thereby the outer peripheral surface of the metal sleeve 12 is formed.
• a seal rubber 22 having a predetermined thickness is formed over substantially the entire surface.
• the thickness of the seal rubber 22 is not particularly limited. However, as described later, the thickness of the seal rubber 22 is smaller than that of the groove (38) for the orifice passage formed in the seal rubber 22. In order to set a sufficient cross-sectional area of the flow channel, it is usually formed with a thickness of 1.5 mm or more.
• the rubber elastic body 14 penetrates through the metal sleeve 12 at a portion located on both sides of the inner cylinder fitting 10 in the eccentric direction with respect to the metal sleeve 12 with the inner cylinder fitting 10 interposed therebetween.
• a first socket part 24 and a second socket 26 are formed on the outer peripheral surface, respectively.
• the metal sleeve 12 is provided with windows 28 at the opening portions of the first and second bracket portions 24 and 26 provided in the rubber elastic body 14, respectively. Through these windows 28, 28, the first and second port capitals 24, 26 open to the outside, respectively. They are humming.
• an annular restricting bracket 30 is embedded and disposed inside the rubber elastic body 14 that constitutes the peripheral wall portion of the first bracket portion 24 so that buckling or the like of the peripheral wall portion is not caused. Regular deformations can be regulated.
• the rubber elastic body 14 constituting the bottom wall of the second bracket 26 has a plurality (3 mm in this embodiment) of voids 32 penetrating in the axial direction. As a result, the spring characteristic of the rubber elastic body 14 is adjusted.
• first and second pocket portions 24, 2 are identical to first and second pocket portions 24, 2
• the seal rubber 22 provided on the outer peripheral surface of the metal sleeve 12 has two ends in the circumferential direction of the windows 28, 28, as shown in FIG.
• the windows 28, 28 are connected to each other to form a concave groove 38, which is opened on the outer peripheral surface and extends in the circumferential direction.
• these grooves 3 8, 5 3 8 correspond to the windows 28, 2 of the metal sleeve 12, respectively.
• 8 is formed in a meandering channel form between the circumferential ends of the windows 8. Therefore, in this embodiment, the circumferential ends ⁇ of both windows 28, 28 are reciprocated by 1.5 times.
• the flow path length is set to about 2.5 times as long as the straight line distance between the two windows 28 and 28 in the circumferential direction Jingdu 1 Yes,
• an outer tube fitting 16 is externally fitted to the integrally vulcanized molded product 20 having such a structure.
• the outer metal bracket 16 is formed in a thick cylindrical shape having an inner diameter larger than the metal sleeve 12 by a predetermined dimension, and has a plurality of mounting holes 40 on its outer peripheral surface.
• the outer tube fitting 16 is attached to the engine unit side or the vehicle body side via the bracket 42.
• the outer cylinder fitting 16 is externally fitted and fixed to the integrally vulcanized molded product 20 as described above, so that the openings of the first and second bolt portions 24 and 26 are formed.
• the first fluid chamber 4 and the second fluid chamber 46 are formed therein, respectively.
• the first and second fluid chambers 4 and 4 are closed by closing the openings of the recessed grooves 38 and 38 formed between the first fluid chamber 4 and the second Orifice passages 4 8 and 4 8 communicating with each other are formed.
• first and second fluid chambers 44 and 46 are filled with a predetermined incompressible fluid such as water, alkylene glycol, polyalkylene glycol, and silicone oil, respectively, and sealed. Have been.
• the sealing of the fluid is performed, for example, by performing an outer fitting operation of the outer cylinder fitting 16 on the integrally vulcanized molded product 20 in a predetermined fluid.
• a sealing rubber is provided between the metal sleeve 12 and the outer cylinder fitting 16. Sufficient fluid tightness can be ensured by pressing the 22.
• the resonance action of the fluid flowing through the orifice passage 48 usually causes a low frequency range around 10 Hz corresponding to an engine shake or a bounce.
• the ratio between the flow cross-sectional area (a) of the orifice passage 48 and the flow path length (£): (a) is tuned so that the high damping effect can be exerted at the time of vibration input.
• the orifice passage 48 is formed in a meandering manner, and the length of the passage (£) is set to be sufficiently large. Therefore, at the time of such tuning, the cross-sectional area (a) of the flow path can be advantageously secured, and therefore, due to the resonance action of the fluid caused to flow through the orifice passage 48. Damping effect Can be effectively exerted.
• the orifice passage 48 is formed of a seal rubber 22 formed on the outer peripheral surface of the metal sleeve 12 and sealing between the outer sleeve 16 and the metal sleeve 12. Since it does not involve the addition of special components, the target engine mount can be provided with good manufacturability and low cost.
• the o and the face passages 48 are formed by the seal rubber 22. Due to the formation of the seal rubber 22, there is a concern that the cross section of the flow passage of the orifice passage 48 may be deformed due to the deformation of the seal rubber 22. Are formed at positions where they are opposed to each other in a direction perpendicular to the vibration input direction and where compression deformation hardly occurs. And the resulting changes in the vibration isolating properties do not become a problem.
• the displacement of the outer cylinder fittings 10 and 16 in the vibration input direction is equal to the outer cylinder fittings 1 of the torsion parts 34 and 36.
• FIGS. 7 and 8 show an engine mount as another embodiment of the present invention.
• members having the same structure as in the above embodiment are denoted by the same reference numerals as those in the above embodiment, and the detailed description thereof will be omitted.
• the present invention is applied to an engine mount having a rectangular block-shaped external shape. This is the application of the light.
• a metal sleeve 50 having a rectangular cylindrical shape is used, and the rainside portion facing the vibration input direction is Each has a window portion 28 through which the first and second pocket portions 24 and 26 formed in the rubber elastic body 14 are opened, while the window portion 28 is perpendicular to the vibration input direction.
• a seal rubber 22 is provided on the outer peripheral surfaces of both sides opposing each other in the direction between the circumferentially opposite ends of the windows 28, 28.
• an orifice passage having a long flow path length can be advantageously formed without increasing the number of special members. Accordingly, as in the first embodiment, an engine mount capable of extremely effectively exhibiting a high damping effect based on the resonance action of a fluid with respect to input vibration in a low frequency range is inexpensive and inexpensive. Be good It can be provided with manufacturability.
• the center of the curved portion in the concave groove 38 forming the orifice passage 48 in the width direction of the flow path is inexpensive and inexpensive.
• a guide plate 54 extending in parallel with the longitudinal direction of the flow path is formed so as to protrude, and the curved portion of the orifice passage 48 is divided into two portions by the guide ⁇ 54 in the width direction. It has been impatient.
• the guide plate 5 is integrally formed by the seal rubber 22 by the seal rubber 22 extending through the rubber bridge 56 formed on the bottom surface of the groove 38 to the center of the groove 38. Is formed.
• the guide plate 54 reduces the ratio (t / R) of the flow path width (t) to the radius of curvature (R) in the curved portion of each orifice passage 48, thereby reducing the flow path resistance. As a result, the resonance effect of the fluid caused to flow in the orifice passage 48 can be more effectively exerted.
• each of the engine mounts in the above-described embodiment has two fluid chambers 44 and 46 in which internal pressure fluctuations are generated at the time of vibration input, respectively. 2 2 4 7 4 6
• one of the fluid chambers can be formed as a variable-capacity equilibrium chamber in which changes in the internal pressure are avoided. It is also possible to form an orifice passage communicating the pressure chamber with the pressure receiving chamber, and the number of these fluid chambers and orifice passages depends on the vibration isolation characteristics required for the mounting device. It is changed as appropriate and is not limited.
• the execution form is not limited to that of the above-described embodiment, but may be determined according to the required anti-vibration characteristics and the like. And may be changed as appropriate.
• seal rubber 22 from the rubber elastic body 14 as a single body, different rubber materials and rubber materials are used for both members so as to satisfy the required sealing performance and vibration damping characteristics. It is also possible to set the characteristics individually.
• the present invention Can be effectively applied to anti-vibration support devices in various mechanical equipment, such as engine mounts for vehicles and other vehicles, and thereby can exhibit excellent anti-vibration performance
• a mold mounting device can be advantageously provided with a simple structure and excellent manufacturability.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Combined Devices Of Dampers And Springs (AREA)

Priority Applications (1)

Applications Claiming Priority (2)

Publications (1)

Family

ID=15626654

Family Applications (1)

Country Status (3)

Cited By (3)

Families Citing this family (1)

Citations (5)

Family Cites Families (8)

• 1988
  • 1988-11-30 JP JP15638888U patent/JPH0276240U/ja active Pending
• 1989
  • 1989-11-29 WO PCT/JP1989/001200 patent/WO1990006455A1/ja active Application Filing
  • 1989-11-29 DE DE3991427T patent/DE3991427T1/de not_active Ceased

Patent Citations (5)

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