JP6408299B2 - Vibration isolator - Google Patents

Description

  The present invention relates to a vibration isolator, and more particularly, to a vibration isolator capable of improving durability and maintaining the effect of suppressing abnormal noise.

  A cylindrical inner cylinder, a cylindrical outer cylinder that surrounds the inner cylinder from the outer peripheral side, a vibration isolating base that connects the inner cylinder and the outer cylinder and is formed of a rubber-like elastic body, and the vibration isolating base 2. Description of the Related Art An anti-vibration device is known that includes a straight portion that penetrates in an axial direction.

  In such an anti-vibration device, for example, in Patent Document 1, a rubber film is provided to connect between the inner wall surfaces of the straight portion, and an abnormal noise (beating) is generated when the inner wall surfaces of the straight portion are pressed together when a displacement is input. A technique for suppressing the generation of noise and rubbing noise is disclosed. In this case, in the technique of Patent Document 1, since the rubber film has a linear shape, the rubber film easily breaks when a large displacement is input in the direction perpendicular to the axis. On the other hand, in the technique disclosed in Patent Document 2, the rubber film is formed in a curved shape, thereby suppressing the breakage of the rubber film when a large displacement is input in the direction perpendicular to the axis.

JP2013-217431A (for example, paragraph 0009, FIG. 4 etc.) JP2013-217405 (for example, paragraph 0013, FIG. 4 etc.)

  However, in the conventional technique described above, even when the rubber film is formed in a curved shape as in Patent Document 2, a sufficient amount of movement of the rubber film cannot be secured, and the large displacement in the direction perpendicular to the axis is not possible. Rubber film easily breaks during input. Moreover, it is easy to fracture | rupture by the displacement input to a twist direction or a twist direction. Therefore, there existed a problem that durability was low and it was difficult to maintain the effect which suppresses abnormal noise.

  The present invention has been made to solve the above-described problems, and an object thereof is to provide a vibration isolator capable of improving durability and maintaining the effect of suppressing abnormal noise.

Means for Solving the Problems and Effects of the Invention

  According to the vibration isolator according to claim 1, the first anti-vibration portion provided in the axial end face on one side of the anti-vibration base and the anti-vibration device while varying the radial position with respect to the first anti-vibration portion. A second curb portion that is recessed in the axial end surface on the other side of the base body, and the first curb portion and the second curb portion are recessed to a position where the respective leading end sides of the base portion overlap each other when viewed in the direction perpendicular to the axis, Since the interposition part is formed between the concave front ends of the first straight part and the second straight part, the inner wall surfaces of the first straight part and the second straight part are crimped when the displacement is input in the direction perpendicular to the axis. The abnormal noise (battering sound and rubbing sound) generated can be suppressed.

In this case, the interposition part is formed between the non-penetrating first straight part and the second straight part of the concave front end side which are arranged at different positions in the radial direction and are alternately recessed vertically. It is possible to secure the degree of freedom of movement of the interposition part and to deform the interposition part with respect to displacement input in each direction. Thereby, it can suppress that an interposed part is fractured | ruptured by the large displacement input to an axis perpendicular direction, and the displacement input to a twist direction or a twist direction. As a result, durability can be improved and the effect of suppressing abnormal noise can be sustained.
At least one or both of the first hollow portions or the second hollow portion, the groove width in the radial direction of the through portion and weight Naru regions overlap with the through portion in the axis-perpendicular direction as viewed in the axis-perpendicular direction viewed Since it is set smaller than the radial groove width dimension outside the region, when the inner wall surfaces of at least one or both of the first and second straight portions are crimped by displacement input in the axial direction, It is easy to form a state in which only the inner surfaces of the region corresponding to the interposition part are first crimped. As a result, it is possible to reduce the area where the inner wall surfaces of at least one or both of the first curving portion and the second curving portion are pressed together, so that it is possible to easily suppress the generation of abnormal noise (sounding sound and rubbing sound).
According to the vibration damping device according to claim 2, wherein, in addition to the effects of the anti-vibration device according to claim 1 wherein the first hollow portion and the second hollow portion is heavy Naru said through portion in the axis-perpendicular direction vision area The groove width dimension in the radial direction is set to be smaller than the groove width dimension in the radial direction in a region other than the region overlapping the interposed part when viewed in the direction perpendicular to the axis, and is positioned on the radially inner side of the first straight part or the second straight part. On the other hand, the radially inner surface of the region overlapping the interposed portion in the radial direction is close to the radially inner surface, and the radial groove width is reduced, and the first straight portion or the second straight portion On the other side located radially outside, the radially inner surface of the region overlapping the interposed portion in the radial direction is close to the radially outer surface and the groove width dimension in the radial direction is reduced. Increasing the width of the installation part, It is possible to improve the resistance. As a result, it is possible to maintain the effect of suppressing the generation of abnormal sounds (striking sounds and rubbing sounds).

  According to the vibration isolator according to claim 3 or 4, in addition to the effect exerted by the vibration isolator according to claim 1 or 2, the recessed tip ends of the first straight part and the second straight part are perpendicular to the axis. In view, it is formed in an arc shape that is convex in the same direction, or is formed in a wave shape that changes substantially in phase with each other. It is possible to secure (enlarge) the free length of the opening portion formed between the concave and leading end sides of the first and second straight portions. Thereby, it can suppress that an interposed part is fractured | ruptured by the large displacement input to an axis perpendicular direction, and the displacement input to a twist direction or a twist direction. As a result, durability can be improved and the effect of suppressing abnormal noise can be sustained.

  In addition, since the free length of the opening portion is expanded, the area where the inner wall surfaces of the first and second straight portions are crimped can be reduced by that amount when a displacement in the direction perpendicular to the axis is input. Generation of (sounding and rubbing sound) can be more reliably suppressed.

(A) is a top view of the vibration isolator in 1st Embodiment, (b) is sectional drawing of the vibration isolator in the Ib-Ib line | wire of Fig.1 (a). (A) is a bottom view of the vibration isolator as viewed in the direction of arrow IIa in FIG. 1 (b), and (b) is a vibration isolator in which the section taken along the line IIb-IIb in FIG. FIG. (A) is the elements on larger scale expansion plan of the vibration isolator in 2nd Embodiment, (b) is the elements on larger scale expanded plan view of the vibration isolator in 3rd Embodiment. (A) is sectional drawing of the vibration isolator in 4th Embodiment, (b) is sectional drawing of the vibration isolator in 5th Embodiment.

  Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings. FIG. 1A is a top view of the vibration isolator 100 according to the first embodiment of the present invention, and FIG. 1B is a cross-sectional view of the vibration isolator 100 taken along line Ib-Ib in FIG. It is. 2A is a bottom view of the vibration isolator 100 as viewed in the direction of arrow IIa in FIG. 1B, and FIG. 2B is a cross-sectional view taken along the line IIb-IIb in FIG. It is the elements on larger scale plane expansion of vibration isolator 100 developed on the plane.

  As shown in FIGS. 1 and 2, the vibration isolator 100 includes a cylindrical inner cylinder 10, a cylindrical outer cylinder 20 that concentrically surrounds the inner cylinder from the outer peripheral side, the inner cylinder 10 and the outer cylinder. 20 and a vibration isolating base 30 formed of a rubber-like elastic body, and a first curving portion 40 and a second curling portion 50 that are recessed in the vibration isolating base 30.

  The first curving portion 40 and the second curling portion 50 are respectively an upper surface (an axial end surface on one side, an upper surface in FIG. 1B) and a lower surface (an axial end surface on the other side) of FIG. b) A non-penetrating recess that is recessed from the lower surface) along the axial direction of the inner cylinder 10 (the vertical direction in FIG. 1 (b)), and a ring concentric with the inner cylinder 10 is divided in the circumferential direction. It is formed in a top view shape.

  A pair of first curled portions 40 are disposed at positions facing each other with the inner cylinder 10 in between (positions whose phases are different by 180 degrees), and the second curled portion 50 has the same phase as the first curled portion 40. A pair is disposed at the position. In addition, the 1st curl part 40 and the 2nd curl part 50 are formed in the range from which the central angle in the axial direction view of the inner cylinder 10 becomes substantially the same angle (in this embodiment, approximately 100 degrees).

  The first curb portion 40 and the second curb portion 50 are disposed with different radial positions (that is, at positions where they do not overlap in the axial direction of the inner cylinder 10). In the present embodiment, the first curb portion 40 is disposed radially inward (inner cylinder 10 side), and the second curb portion 50 is disposed radially outward (outer cylinder 20 side).

  In this case, the first straight portion 40 and the second straight portion 50 are recessed to a position where the respective recessed leading ends overlap when the inner cylinder 10 is viewed in the direction perpendicular to the axis. That is, an overlapping margin that overlaps along the axial direction of the inner cylinder 10 is formed on the recessed distal end side of the first and second straight portions 40 and 50. An interposition part 31 is formed between the recessed tip ends of the first and second curb portions 40 and 50.

  In the present embodiment, the recessed depths of the first curving portion 40 and the second curling portion 50 are set to be constant along the circumferential direction. Therefore, the interposition part 31 is orthogonal to the axial direction of the inner cylinder 10 while having a certain width (dimension in the vertical direction in FIG. 2B) in the flat developed state (see FIG. 2B). It is formed in a strip shape extending linearly in the direction.

  According to the vibration isolator 100, since the interposition part 31 is formed between the recessed front end sides of the first and second curb portions 40 and 50, the direction perpendicular to the axis (the left-right direction in FIG. 1B). The noise (battering sound and rubbing sound) generated when the inner wall surfaces of the first curving portion 40 and the second curling portion 50 are pressure-bonded when the displacement is input can be suppressed.

  In this case, the interposition part 31 does not connect the inner wall surfaces of the straight part formed so as to penetrate as in the conventional product, but is arranged in a radially different position and is alternately recessed vertically. Since it is formed between the recessed front end side of the first straight part 40 and the second straight part 50, the degree of freedom of movement of the interposition part 31 is ensured, and the interposition is provided for displacement input in each direction. The part 31 can be deformed. Thereby, it can suppress that the interposed part 31 is fractured | ruptured by the large displacement input to an axis orthogonal direction, and the displacement input to a twist direction or a twist direction. As a result, durability can be improved and the effect of suppressing abnormal noise can be sustained.

  Next, with reference to FIG. 3, the vibration isolators 200 and 300 in the second and third embodiments will be described. FIG. 3A is a partially enlarged plan development view of the vibration isolation device 200 in the second embodiment, and FIG. 3B is a partial enlarged plan development view of the vibration isolation device 300 in the third embodiment. 3A and 3B correspond to a state in which the cross section taken along the line IIb-IIb in FIG. Moreover, the same code | symbol is attached | subjected to the part same as 1st Embodiment, and the description is abbreviate | omitted.

  As shown in FIG. 3A, in the vibration isolator 200 according to the second embodiment, the recessed depth of the first straightened portion 240 is gradually increased from the circumferential end toward the circumferential center. On the other hand, the recessed depth of the second curb portion 250 is gradually decreased from the circumferential end toward the circumferential center. As a result, the interposition part 231 is formed in a belt-like shape extending in a circular arc shape while having a substantially constant width in the planar development state.

  As shown in FIG. 3B, in the vibration isolator 300 according to the third embodiment, the recessed depth of the first straight portion 340 is periodically increased and decreased in a wave shape from one end to the other end in the circumferential direction. The Similarly, the recessed depth of the second curb portion 350 is periodically increased and decreased in a wave shape from one end to the other end in the circumferential direction in the same phase as the increase / decrease in the first curb portion 340. As a result, the interposition part 331 is formed in a wave-like belt-like shape extending in a curved manner and having a substantially constant width in a planar development state.

  As described above, according to the second and third embodiments, the interposition portions 231 and 331 are formed in an arc shape or a wave shape in a planar development state. Thus, the free length can be secured (enlarged). Thereby, it is possible to prevent the interposed portions 231 and 331 from being broken by a large displacement input in the direction perpendicular to the axis and a displacement input in the twisting direction or the twisting direction. As a result, durability can be improved and the effect of suppressing abnormal noise can be sustained.

  In addition, since the free length of the interposed portions 231 and 331 is increased in this way, the area of the interposed portions 231 and 331 is increased, and accordingly, the first straight portion 240 is input at the time of displacement input in the direction perpendicular to the axis. , 340 and the second straight portions 250, 350 can be reduced in the area where the inner wall surfaces are crimped together, so that the generation of abnormal noise (sounding and rubbing sound) can be more reliably suppressed.

  Next, with reference to FIG. 4, vibration isolators 400 and 500 in the fourth and fifth embodiments will be described. FIG. 4A is a cross-sectional view of the vibration isolator 400 according to the fourth embodiment, and FIG. 4B is a cross-sectional view of the vibration isolator 500 according to the fifth embodiment. 4A and 4B correspond to FIG. 1B. Also, the same parts as those in the above embodiments are denoted by the same reference numerals, and description thereof is omitted.

  As shown in FIG. 4A, in the vibration isolator 400 according to the fourth embodiment, a bulging portion 434 is formed on the inner wall surface of the first curled portion 440 on the inner cylinder 10 side. The groove width dimension (the dimension in the radial direction of the inner cylinder 10, the dimension in the left-right direction in FIG. 4A) is partially narrowed on the leading end side of the recess. On the other hand, the second curled portion 450 is formed with a bulged portion 435 on the inner wall surface on the outer cylinder 20 side, and the groove width dimension of the second curled portion 450 is partially narrowed on the concave front end side.

  As shown in FIG. 4B, in the vibration isolator 500 according to the fifth embodiment, a bulging portion 534 is formed on the inner wall surface of the first curled portion 540 on the outer cylinder 20 side, and the first curled portion 540 The groove width dimension (the dimension in the radial direction of the inner cylinder 10, the dimension in the left-right direction in FIG. 4B) is partially narrowed on the leading end side of the recess. On the other hand, the second curled portion 550 has a bulged portion 535 formed on the inner wall surface on the inner cylinder 10 side, and the groove width dimension of the second curled portion 550 is partially narrowed on the recessed tip end side.

  In the present embodiment, the bulging portions 434, 435, 534, and 535 are continuously formed from one end to the other end in the circumferential direction of each of the straight portions 440, 450, 540, and 550.

As described above, according to the fourth and fifth embodiments, the groove width dimensions of the first straight portions 440 and 540 and the second straight portions 450 and 550 (the horizontal dimension in FIGS. 4A and 4B). Is reduced on the leading end side of the recessed portion, that is, the groove width dimension in the region corresponding to the interposition portions 31 and 531 is narrowed. When the inner wall surfaces of the straight portions 450 and 550 are pressure-bonded, the inner wall surfaces in the region corresponding to the interposition portions 31 and 531 can be pressure-bonded first, and abnormal noise (sounding and rubbing sound) is generated. In addition, as in the fifth embodiment, the first curb portion 540 has an inner wall surface on the outer cylinder 20 side, and the second curb portion 550 has an inner wall surface on the inner cylinder 10 side, as in the fifth embodiment. When the bulging portions 534 and 535 are formed, respectively, the interposed portion 5 Since the width dimension 31 (dimension in the left-right direction in FIG. 4B) can be increased, the durability can be improved accordingly. As a result, the effect of suppressing abnormal noise can be sustained.

  As described above, the present invention has been described based on the embodiments, but the present invention is not limited to the above-described embodiments, and various improvements and modifications can be easily made without departing from the spirit of the present invention. It can be guessed.

  It is naturally possible to combine part or all of the configuration in each of the above embodiments with part or all of the configuration in the other embodiments.

  The numerical values given in the above embodiments are examples, and other numerical values can naturally be adopted. For example, in each of the above-described embodiments, the case has been described in which the number of the arranged straight portions including the first straight portion 40 to 540 and the second straight portion 50 to 550 is two sets. It can be set arbitrarily and may be one set or three or more sets.

  In each of the above-described embodiments, the case where the second straightening portions 50 to 550 are formed on the radially outer side with respect to the first straightening portions 40 to 540 has been described. However, the present invention is not necessarily limited thereto. The second straight portions 50 to 550 may be formed on the radially inner side with respect to the straight portions 40 to 540.

  In each of the above-described embodiments, the case has been described in which the first straight portions 40 to 540 and the second straight portions 50 to 550 have the same central angle as viewed in the axial direction of the inner cylinder 10. It is not restricted to this, It is good also considering the one central angle of the 1st straight part 40-540 or the 2nd straight part 50-550 as an angle different from the other central angle.

  In each of the above embodiments, the case where the flange is formed at one end in the axial direction of the outer cylinder 20 has been described. However, the present invention is not necessarily limited thereto, and the flange may be omitted. Similarly, in each of the above-described embodiments, the case where the inner cylinder 10 and the outer cylinder 20 are formed in a circular cross section has been described. Further, a bulge shape (bulge) that bulges radially outward may be formed on the outer surface of the inner cylinder 10.

  In the second embodiment, the case where the interposition part 231 is formed to be curved in an arc shape in the planar development state has been described. However, the present invention is not necessarily limited thereto. It may be formed in a letter shape.

  In the third embodiment, the case where the interposition part 331 is formed in a wave shape in the planar development state has been described. However, the present invention is not necessarily limited to this, and for example, it is formed in a saw blade shape. There may be. The number of waves or blades in the wave shape or saw blade shape is arbitrary.

  In the fourth and fifth embodiments, the case has been described in which the bulging portions 434, 435, 534, and 535 are formed on the inner wall surfaces of both the first and second straight portions 440 and 540 and 450 and 550, respectively. However, the present invention is not necessarily limited to this, and the bulging portions 434, 435 or the bulging portions 534, 535 are formed only on the inner wall surface of either the first curling portion 440, 540 or the second curling portion 450, 550. It may be a thing.

100, 200, 300, 400, 500, anti-vibration device 10 inner cylinder 20 outer cylinder 30 anti-vibration bases 31, 231, 331, 531 interposition part 40, 240, 340, 440, 540 first straight part 50, 250, 350, 450, 550 Second curb

Claims (4)

An anti-vibration device comprising: a cylindrical inner tube; a cylindrical outer tube that surrounds the inner tube from the outer peripheral side; and an anti-vibration base that connects the inner tube and the outer tube and is formed of a rubber-like elastic body. In the device
A first curving portion that is recessed in an axial end surface on one side of the vibration-proof base;
A second curb portion that is recessed in the axial end surface on the other side of the vibration isolating base while varying a radial position with respect to the first curb portion,
The first straight part and the second straight part are recessed to a position where the concave front ends overlap each other when viewed in the direction perpendicular to the axis, and are interposed between the concave front ends of the first straight part and the second straight part. Part is formed,
Wherein at least one or both of the first hollow portions or the second hollow portion, the area where the groove width of the through portion and radially in the heavy Naru region in the direction perpendicular to the axis vision overlaps the through portion in the axis-perpendicular direction viewed An anti-vibration device characterized by being set smaller than the radial groove width dimension in other than the above . Wherein the first hollow portion and the second hollow portion, the groove width in the radial direction of the through portion and weight Naru region in the axis-perpendicular direction when viewed from the radial direction in the region other than the region overlapping with the through portion in the axis-perpendicular direction viewed Set smaller than the groove width dimension ,
One of the first curb portion and the second curb portion located on the radially inner side has a radially outer inner surface adjacent to the radially inner inner surface of the region overlapping the interposed portion in the radial direction. The groove width dimension is reduced,
The other of the first curving portion and the second curving portion, which is located on the radially outer side, has a radially inner surface adjacent to the radially outer inner surface of the region overlapping the interposed portion in the radial direction. The vibration isolator according to claim 1, wherein the groove width dimension is reduced.   3. The prevention according to claim 1, wherein the concave tip ends of the first straight part and the second straight part are formed in a curved shape that is convex in the same direction when viewed in the direction perpendicular to the axis. Shaker. The anti-vibration device according to claim 1 or 2, wherein the concave tip ends of the first and second straight portions are formed in wave shapes that change in substantially the same phase when viewed in the direction perpendicular to the axis.

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