JP2008002565A - Vibration absorbing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vibration absorbing device improved in vibration absorbing effects during idling input, also improved in durability, and makes less booming noises during acceleration input, by reducing a dynamic spring constant in a suspending direction. <P>SOLUTION: When an engine is suspended and supported, a first gap is formed between an intermediate rubber member 4 and a body rubber member 3. So, the dynamic spring constant is reduced in the suspending direction to improve vibration absorbing effects during idling input. On the other hand, in great displacement exceeding the first gap, the body rubber member 3 and the intermediate rubber member 4 are both deformed to suppress the distortion of the body rubber member 3 and improve the durability thereof. Besides, in lateral displacement of an insertion-through member 5 during acceleration input, the sudden rise of the dynamic spring constant is avoided by increasing the thickness size in the displacing direction by an equivalent for the intermediate rubber member 4 to suppress the occurrence of booming noises. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to an anti-vibration device for hanging and supporting an engine, and in particular, by reducing the dynamic spring constant in the hanging direction and improving the anti-vibration effect at the time of idling input, while improving durability and at the time of acceleration input The present invention relates to an anti-vibration device capable of suppressing a booming noise.

  When attaching a vibration generator such as an automobile engine to a vehicle body frame, conventionally, a vibration isolator is interposed between the vibration generator and the vehicle frame so that the vibration of the vibration generator is transmitted to the vehicle frame. Is preventing.

  As this anti-vibration device, there is known an anti-vibration device that supports an anti-vibration in a state where a vibration generating body such as an engine is suspended from a body frame by a suspension member (Patent Document 1). An example of such a suspended vibration isolator is shown in FIG.

  As shown in FIG. 14, the conventional suspension type vibration isolator is composed of an upper substrate 101, a lower substrate 102 having an opening 102a, the upper substrate 101 and the lower substrate 102, and a rubber-like elastic material. And a main body rubber member 103.

And as shown in FIG. 14, while attaching the lower board | substrate 102 to the vehicle body frame BF, one end of the suspension member 104 inserted in the opening part 102a of the lower board | substrate 102 is connected with the upper board | substrate 102, and the other end is engine. By connecting to the side (not shown), the engine is supported while being suspended from the vehicle body frame BF.
JP-A-2004-69038 (FIG. 1 etc.)

  Incidentally, in the case of the above-described suspension type vibration isolator, the dynamic spring constant in the suspension direction (vertical direction in FIG. 14) is as small as possible in order to obtain the vibration isolation effect during idling more effectively. Is preferred. For this reason, the main body rubber member 103 needs to have a thin thickness dimension at a portion located between the opening 102 a and the suspension member 104.

  However, in the suspension-type vibration isolator, the suspension member 104 is brought into contact with the inner peripheral surface of the main rubber member 103, so that the displacement of the engine (for example, the vehicle longitudinal direction during sudden acceleration or an accidental load (see FIG. 14 is a structure that regulates displacement in the left-right direction).

  Therefore, if the thickness dimension of the part located between the opening 102a and the suspension member 104 is made thin, the dynamic spring constant is set when receiving the displacement of the suspension member 104 in order to restrict the displacement of the engine. There was a problem that it suddenly rose and a muffled noise was generated. Moreover, if the thickness dimension of the said site | part is made thin, the distortion amount of the main body rubber member 103 will become large, and there existed a problem that the fall of durability was caused.

  The present invention has been made to solve the above-described problems. The dynamic spring constant in the hanging direction is reduced to improve the anti-vibration effect during idling input, while improving durability and acceleration input. An object of the present invention is to provide an anti-vibration device capable of suppressing the squeaking noise.

  In order to achieve this object, the vibration isolator according to claim 1 is a main body constituted by an upper member, a base member having an opening, and the upper member and the base member and a rubber-like elastic material. A rubber member, and attaching the base member to the vehicle body frame side, connecting one end of the insertion member inserted through the opening of the base member to the upper member, and connecting the other end to the engine side. The engine is suspended from the vehicle body frame, and is disposed between the main body rubber and the base member, and an intermediate rubber member made of a rubber-like elastic material; and the base member A stopper rubber portion disposed on the upper surface and abutting against the lower surface of the upper member when a large displacement is input, and the base member includes a bottom plate portion where the opening portion is opened, and a cylindrical outer member rising from the bottom plate portion. Tube part and outward from the upper end of the outer cylinder part An outer member having an attachment plate portion attached to the vehicle body frame side, a cylindrical inner cylinder portion having an outer diameter corresponding to an inner diameter of the outer cylinder portion of the outer member, and the inner cylinder portion A projecting plate portion projecting outward from the upper end and superposed on the mounting plate portion of the outer member, and a main body member to which the main body rubber member is connected, and the outer cylinder portion of the outer member includes the body member The inner cylinder portion of the main body member is press-fitted into the inner member, so that the outer member and the main body member are integrally formed, and the stopper rubber portion is connected to the upper surface of the protruding plate portion of the main body member, The intermediate rubber member is integrally formed with the main body rubber member, and the intermediate rubber member includes an insertion hole through which the insertion member is inserted, and is disposed on an upper surface of a bottom plate portion of the outer member, and the engine is mounted on the body frame. In the suspended support state, the intermediate rubber member And a lower surface of the main rubber member, a first gap is formed, and the first gap is larger than a second gap formed between the stopper rubber portion and the lower surface of the upper member. It is comprised so that it may become small.

  The vibration isolator according to claim 2 is the vibration isolator according to claim 1, wherein a third gap is formed between the upper surface of the bottom plate portion of the outer member and the lower surface of the main body member or the main body rubber member. The intermediate rubber member includes a lip portion projecting outward from an outer edge of the seating surface abutted against the bottom plate portion, and the lip portion is located in the third gap.

  The vibration isolator according to claim 3 is the vibration isolator according to claim 2, wherein the opening portion opened in the bottom plate portion is formed in an oval shape, and the major axis direction of the oval shape is accelerated. The intermediate rubber member is positioned along the displacement direction at the time of input, and the intermediate rubber member has a seat surface that is in contact with the bottom plate portion formed in a circular shape having an outer diameter larger than the dimension in the major axis direction of the opening. The four divided body portions are formed between the slits by extending slits at four locations from the center portion to the center portion, and the four divided body portions are a pair positioned on the long axis of the opening portion. The first divided body part and a pair of second divided body parts located across the major axis of the opening, and the width of the first divided body part is that of the second divided body part. It is shorter than the width dimension.

  The vibration isolator according to claim 4 is the vibration isolator according to claim 3, wherein the slit extends to a position reaching the opening of the bottom plate.

  The vibration isolator according to claim 5 is the vibration isolator according to any one of claims 1 to 4, wherein the intermediate rubber portion projects from the seating surface, and when the large displacement is input, The clamped part is sandwiched between the opening part, and the clamped part is located apart from the inner edge of the opening part. Anti-vibration device.

  According to the vibration isolator of claim 1, the base member is attached to the vehicle body frame side, one end of the insertion member inserted through the opening of the base member is connected to the upper member, and the other end is on the engine side. The engine is supported in a suspended manner with respect to the vehicle body frame.

  In this suspended state, the engine load is supported only by the main body rubber member, and the main body rubber member performs a vibration damping function and a vibration insulation function, so that the vehicle body frame for idling vibration input from the engine. Transmission to is suppressed.

  On the other hand, when a large displacement vibration is input in the hanging direction, the main rubber member is displaced until it comes into contact with the intermediate rubber member, and both the main rubber member and the intermediate rubber member are simultaneously deformed. And if the vibration of the large displacement to this suspending direction is further input, a stopper effect | action will be exhibited because an upper member will contact | abut to a stopper rubber part.

  Further, when the insertion member is displaced in the lateral direction in accordance with the displacement of the engine during acceleration input, the displacement of the insertion member is received not only by the main rubber member but also by the intermediate rubber member. And the intermediate rubber member are deformed to restrict the displacement.

  As described above, according to the vibration isolator of the present invention, the main body rubber member and the intermediate rubber member are configured separately, and only the main body rubber member functions at the time of idling input (the intermediate rubber member does not function). Since both the main rubber member and the intermediate rubber member function at the time of input or large displacement input, while improving the anti-vibration effect at the time of idling input, improving its durability and suppressing the muffled noise at the time of acceleration input There is an effect that it can be planned.

  That is, according to the present invention, the intermediate rubber member is configured separately from the main body rubber member, the intermediate rubber member is disposed between the main body rubber member and the base member, and the engine is suspended from the body frame. In the lowered support state, since the first gap is formed between the upper surface of the intermediate rubber member and the lower surface of the main rubber member, only the main rubber member contributes to the support of the engine load. Since the contribution of the rubber member can be avoided, the dynamic spring constant in the suspending direction can be reduced correspondingly, thereby improving the vibration-proofing effect at the time of idling input.

  Here, if the spring constant in the suspension direction is reduced to obtain the vibration isolation effect at the time of idling input, the displacement amount (strain amount) of the main rubber member per unit load increases, so the distortion at the time of large displacement vibration input. There is a problem that the amount becomes excessive, and the durability of the main rubber member is reduced accordingly.

  On the other hand, according to the present invention, since the intermediate rubber member is disposed on the upper surface of the bottom plate portion of the outer member, a large displacement vibration exceeding the first gap is input in the hanging direction. However, the main rubber member comes into contact with the intermediate rubber member, and both the main rubber member and the intermediate rubber member are deformed together to receive the input.

  As a result, when idling is input, only the main rubber member contributes and the dynamic spring constant is reduced to ensure the vibration-proof effect, while at the time of large displacement vibration input, the intermediate rubber member is also added to the main rubber member. By contributing, there is an effect that the amount of distortion of the main rubber member can be suppressed and the durability can be improved.

  According to the present invention, the stopper rubber portion that contacts the lower surface of the upper member when a large displacement is input is disposed on the upper surface of the base member, and the second rubber formed between the stopper rubber portion and the lower surface of the upper member. Since the gap 2 is configured to be larger than the first gap, the lower surface of the upper member is brought into contact with the stopper rubber portion even when vibration exceeding the large displacement vibration described above is further input. Thus, the input of a large displacement can be restricted. As a result, the amount of distortion of the main rubber member and the intermediate rubber member can be suppressed, and the durability can be improved.

  Here, unlike the conventional product, if the intermediate rubber member is not provided and only the main body rubber member is used, it is difficult to secure the thickness dimension of the portion that receives the lateral displacement of the insertion member (this thickness). Increasing the dimension increases the spring constant in the suspension direction as described above, leading to a decrease in the vibration isolation effect during idling.) To regulate the displacement of the engine during acceleration input, the displacement of the insertion member is reduced. When it is received, there is a problem that the dynamic spring constant increases rapidly and a muffled noise is generated.

  On the other hand, according to the present invention, the intermediate rubber member has an insertion hole for inserting the insertion member, and the intermediate rubber member is disposed on the upper surface of the bottom plate portion of the outer member, that is, the outer cylinder of the outer member. Since the intermediate rubber member is positioned in the space formed on the inner peripheral side of the portion (and the inner cylinder portion of the main body member), when the insertion member is displaced laterally, the insertion member and the outer The intermediate rubber member can be pressed between the inner peripheral side of the cylindrical portion.

  That is, when the insertion member is displaced laterally with the displacement of the engine at the time of acceleration input, the displacement of the insertion member is not only received by the main rubber member but also the intermediate rubber member. Since it can be received, the thickness dimension in the displacement direction can be increased by the amount corresponding to the intermediate rubber member, and a sudden increase in the dynamic spring constant can be avoided.

  As a result, when idling input, as described above, only the main rubber member contributes and the dynamic spring constant is reduced to ensure the vibration isolation effect, while at the time of acceleration input, intermediate rubber is added to the main rubber member. By making the contribution of the member and securing the thickness of the rubber member in the lateral direction, it is possible to suppress the sudden increase in the dynamic spring constant due to the displacement in the lateral direction, and to generate a booming noise during acceleration input. There is an effect that can be suppressed.

  Thus, there is a conflicting relationship between the improvement of the anti-vibration effect at idling and the suppression of the muffled noise and the improvement of the durability at the time of acceleration input, both of which cannot be achieved with the configuration of the conventional product. As in the present invention, the main rubber member and the intermediate rubber member are configured separately and can be achieved only by separating the inputs to which they contribute.

  In addition, according to the vibration isolator of the present invention, the base member includes the outer member and the main body member, and the inner cylinder portion of the main body member is press-fitted into the outer cylinder portion of the outer member. Even if it is configured separately from the main rubber member, the intermediate rubber member can be easily disposed between the main rubber member and the bottom plate portion in the step of integrating the base member (press-fitting step). As a result, there is an effect that the assembly work can be facilitated and the number of assembling steps can be reduced as the whole vibration isolator.

  In addition, since the body member is formed with the projecting plate portion projecting outward at the upper end of the inner cylinder portion, when the inner cylinder portion of the body member is press-fitted into the outer cylinder portion of the outer member ( In the press-fitting step), the press-fitting direction positioning (adjustment of press-fitting amount) can be easily performed by press-fitting to the position where the overhanging plate portion of the main body member overlaps with the attachment plate portion of the outer member. As a result, there is an effect that the press-fitting work can be facilitated and the assembly man-hours of the entire vibration isolator can be reduced.

  Further, the above-described stopper rubber portion is arranged on the upper surface of the overhanging plate portion. Since this overhanging plate portion is a portion that is superposed on the mounting plate portion of the outer member, these overhanging plate portions are used. There exists an effect that the intensity | strength can be ensured by two-sheet superimposition with a board part and an attachment board part. Furthermore, the overhanging plate portion is not provided over the entire circumference, but is provided only at a position corresponding to the stopper rubber portion, so that the strength of the portion functioning as the stopper portion is secured by the above-described polymerization effect. However, since the other sites are not polymerized, there is an effect that the weight can be reduced accordingly.

  According to the vibration isolator according to claim 2, in addition to the effect of the vibration isolator according to claim 1, the intermediate rubber member has a lip portion projecting outward from the outer edge of the seating surface in contact with the bottom plate portion. For example, with the lateral displacement of the insertion member during acceleration input, the intermediate rubber member is moved toward the displacement direction, and the intermediate rubber member is returned from the movement direction toward the opposite direction. In this case, the lip portion serves as a guide, so that the outer edge on the return direction side fits into the opening of the bottom plate portion and cannot return to the initial position, or the fitted portion is damaged. There is an effect that can be avoided in advance.

  Furthermore, according to the vibration isolator of the present invention, the third gap is formed between the upper surface of the bottom plate portion of the outer member and the lower surface of the main body member or the main body rubber member, and the space formed by the third gap. Since the lip portion is arranged inside, there is an effect that it is possible to effectively use a useless space which becomes a dead space.

  Thus, by providing the lip portion, the outer diameter of the intermediate rubber member is reduced, leading to a decrease in durability, or the volume of the intermediate rubber member (outer diameter) is secured in order to secure the base member ( With the increase in the diameter of the inner cylinder part and the outer cylinder part), it is possible to avoid the problem that the vibration isolator as a whole is enlarged, and as a result, while preventing the vibration isolator as a whole from becoming large There is an effect that the volume of the intermediate rubber member is secured, and the above-described improvement in durability and the suppression of the muffled noise during acceleration input can be efficiently achieved.

  According to the vibration isolator according to claim 3, in addition to the effect produced by the vibration isolator according to claim 2, the displacement direction when the major axis direction is the acceleration input during the acceleration input (that is, the insertion member) And the seating surface of the intermediate rubber member that is in contact with the bottom plate part is formed in a circular shape having a diameter larger than the dimension in the major axis direction of the opening. While securing the displaceable area of the member, the contact area between the seating surface and the bottom plate of the intermediate rubber member is expanded to improve the durability of the intermediate rubber member and to reduce the size of the vibration isolator as a whole. There is an effect that it can be planned.

  That is, when the contact area between the seating surface of the intermediate rubber member and the bottom plate portion cannot be ensured, the displacement (amount of strain) of the intermediate rubber member becomes large when inputting a large displacement in the hanging direction. On the other hand, when the contact area between the seating surface of the intermediate rubber member and the bottom plate is widened, the durability can be improved, but the size of the vibration isolator as a whole is increased. There is a problem. In addition, when the opening area of the opening portion is reduced, it is possible to obtain an increase in size and a contact area, but there is a problem that a region necessary for the movement of the insertion member cannot be secured. .

  On the other hand, according to the vibration isolator of the present invention, the opening is formed in an oval shape in which the long axis direction is the moving direction of the insertion member at the time of acceleration input, so a region necessary for the movement of the insertion member is secured. However, the opening area of the opening can be further reduced. And while the opening is formed in an oval shape, the seating surface of the intermediate rubber member is formed in a circular shape, so that the contact area between the seating surface of the intermediate rubber member and the bottom plate portion is reduced while reducing the size of the intermediate rubber member. Can be secured as efficiently as necessary. As a result, the above-described problems can be solved.

  Here, according to the vibration isolator of the present invention, as described above, along with the lateral displacement of the insertion member during acceleration input, the intermediate rubber member is moved in the displacement direction, and the movement is also performed. When the intermediate rubber member attempts to return from the direction to the opposite direction, the lip portion serves as a guide, thereby preventing the outer edge of the intermediate rubber member from entering the opening.

  However, when the displacement at the time of acceleration input is large, the eccentric deformation of the intermediate rubber member is large, so that the lip portion is inclined and wrinkled, and the lip portion cannot sufficiently exert the role of the guide. .

  On the other hand, according to the vibration isolator of the present invention, four slits are extended from the outer edge of the intermediate rubber member toward the center portion, and four divided body portions are formed between these slits. Since the lip portion is divided at four locations, the displacement at the time of acceleration input is large, and even if the intermediate rubber member is greatly eccentrically deformed as the insertion member moves in the lateral direction, the lip portion is Since it is not continuous in the circumferential direction, it is possible to effectively suppress the inclination and wrinkle of the lip portion due to the eccentric deformation and to sufficiently exert the role as a guide in the lip portion.

  In addition, the slit is not divided only at the lip portion, but is configured to extend the slit to a position beyond the lip portion (a configuration in which four divided body portions are formed), so that the intermediate rubber member is greatly eccentrically deformed. In this case, it is possible not only to prevent the lip portion from tilting and wrinkling but also to suppress the deformation of the intermediate rubber member itself. In particular, it is difficult for the deformation of the part on the eccentric direction side to affect the part on the opposite side to the eccentric direction, and the part on the opposite side to the eccentric direction (particularly, the divided body part) should maintain the initial shape. it can. As a result, it is possible to effectively suppress the inclination and wrinkle of the lip portion due to the eccentric deformation, and to make the lip portion serve as a guide more reliably.

  Here, since the opening is formed in an oval shape, the intermediate rubber member is greatly eccentrically deformed in the long axis direction of the opening. Since the width dimension of the pair of first divided body parts located on the long axis of the part is shorter than the width dimension of the pair of second divided body parts located across the long axis of the opening, the intermediate rubber Even when the member is greatly eccentrically deformed in the major axis direction of the opening, it is possible to further exert an effect of maintaining the initial shape of the portion opposite to the eccentric direction. As a result, it is possible to effectively suppress the inclination and wrinkle of the lip portion due to the eccentric deformation, and to make the lip portion serve as a guide more reliably.

  According to the vibration isolator according to claim 4, in addition to the effect of the vibration isolator according to claim 3, the slit is extended to the position reaching the opening of the bottom plate portion, thereby suppressing the generation of abnormal noise. There is an effect that can be.

  That is, when the lower surface of the main rubber member comes into contact with and presses the upper surface of the intermediate rubber member with the input of large displacement vibration in the hanging direction, the air left between the two rubber members is compressed. In addition, the compressed air is discharged to the outside at a stroke from between the contact surfaces of the main rubber member and the intermediate rubber member, so that an abnormal noise is generated. Thus, a path for escaping the air left between the two rubber members to the outside is secured, so that the air can be prevented from being compressed and the generation of abnormal noise can be suppressed. There is.

  According to the vibration isolator described in claim 5, in addition to the effect of the vibration isolator described in claim 4, the clamped portion is protruded from the seat surface portion of the intermediate rubber portion so that a large displacement in the lateral direction is input. Since the sandwiched portion is configured to be sandwiched between the insertion member and the inner edge of the opening, the impact when the insertion member collides with the inner edge of the opening is absorbed by the sandwiched portion, and the hitting sound is generated. There is an effect that it is possible to suppress the occurrence of.

  Furthermore, since the sandwiched portion is configured to be spaced apart from the inner edge of the opening, when the insertion member collides with the inner edge of the opening, the sandwiched portion is moved from the opening to the bottom plate portion. There is an effect that it is possible to suppress the inconvenience that the clamped portion that has climbed on the upper surface does not return from the upper surface of the bottom plate portion into the opening. As a result, the effect of suppressing the hitting sound can be stably exhibited.

  DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, preferred embodiments of the invention will be described with reference to the accompanying drawings. FIG. 1 is a front view of a vibration isolator 100 according to the first embodiment of the present invention, and FIG. 2 is a partial cross-sectional perspective view of the vibration isolator 100. 3 is a top view of the vibration isolator 100, and FIG. 4 is a cross-sectional view of the vibration isolator 100 taken along line IV-IV in FIG.

  1 to 4 illustrate a state in which the engine is supported by the vibration isolator 100 in a suspended manner. In addition, in order to simplify the drawing and facilitate understanding, FIGS. 2 to 4 show a state in which the fastening nut 61 and the fastening bolt 62 are omitted. In FIG. It is illustrated virtually.

  As shown in FIGS. 1 to 4, the vibration isolator 100 attaches the base member 2 to the vehicle body frame BF, and uses the upper member 1 as one end of the insertion member 5 inserted through the opening 22 a of the base member 2. By connecting and connecting the other end to the engine side member EM, the vibration of the engine is transmitted to the vehicle body frame BF by supporting the engine (not shown) in a suspended manner with respect to the vehicle body frame BF. It is an apparatus for preventing, and mainly comprises an upper member 1, a base member 2, a main body rubber member 3, and an intermediate rubber member 4.

  As shown in FIGS. 2 and 4, the upper member 1 includes a boss member 1a to which a main body rubber member 3 to be described later is vulcanized and bonded, and a flat plate member 1b connected and fixed to the upper end surface of the boss member 1a. Configured. The boss member 1a is formed of a steel material in a substantially truncated conical shape with a constricted cross section symmetric about the axis O, and the flat plate member 1b is formed in a horizontally long flat plate shape.

  As shown in FIGS. 2 and 4, the boss member 1 a and the flat plate member 1 b are provided with insertion holes 11 a and 11 b drilled along the axis O, respectively, and will be described later in the insertion holes 11 a and 11 b. The insertion member 5 is inserted, and the fastening nut 61 is fastened to the tip (upper side in FIG. 2), whereby the boss member 1a and the flat plate member 1b are connected and fixed.

  As shown in FIGS. 2 and 4, the insertion hole 11a of the boss member 1a includes a small diameter portion and a large diameter portion, and a step formed between the small diameter portion and the large diameter portion The step of the insertion member 5 is received and positioning in the direction of the axis O is performed.

  As shown in FIGS. 1 to 4, the base member 2 includes an outer member 21 attached to the body frame BF, and a main body that is press-fitted into the outer member 21 and is connected to a main rubber member 3 described later. The outer member 21 and the main body member 25 are each formed of a steel material in a substantially cup shape.

  As shown in FIGS. 2 and 4, the external member 21 rises upward (upward in FIG. 4) from the outer edge of the bottom plate portion 22 where the opening 22 a is formed, and the bottom plate portion 22, and around the axis O. The outer cylinder part 23 is formed in a symmetrical cylindrical shape, and the mounting plate part 24 is formed to project outward from the upper end (upper end in FIG. 4) of the outer cylinder part 23. .

  As shown in FIGS. 1 to 4, the attachment plate portion 24 has through holes 24 a formed at two locations on both ends in the longitudinal direction, and the fastening bolts 63 inserted through the through holes 24 a It is attached (fastened and fixed) to the frame BF.

  As shown in FIGS. 2 and 4, the main body member 25 includes a cylindrical inner cylinder portion 26 having an outer diameter corresponding to the inner diameter of the outer cylinder portion 23 of the outer member 21, and an upper end of the inner cylinder portion 27 (see FIG. (4 upper end) and a projecting plate portion 27 formed to project outward.

  2 and 4, the inner cylinder portion 26 of the main body member 25 is press-fitted into the outer cylinder portion 23 of the outer member 21 so that the main body portion 25 and the outer member 21 are integrated. Composed. Further, the projecting plate portion 27 of the main body portion 25 is superposed on the attachment plate portion 24 of the outer member 21 and, as shown in FIG. 3, only a portion where a later-described stopper rubber portion 3a is disposed is partially provided. It is greatly formed outward.

  Thus, since the body member 25 is formed with the projecting plate part 27 projecting outward at the upper end of the inner cylinder part 26, the inner cylinder part 26 is press-fitted into the outer cylinder part 23 of the outer member 21. In the press-fitting process, the press-fitting direction positioning (adjustment of the press-fitting amount) can be easily performed by press-fitting to the position where the overhanging plate part 27 overlaps the attachment plate part 24 of the outer member 21. As a result, the press-fitting work can be facilitated, and the assembly man-hours of the vibration isolator 100 as a whole can be reduced.

  Further, as will be described later, the overhanging plate portion 27 is a member constituting a portion where the stopper rubber portion 3b is disposed on the upper surface and the strength is required. As shown in FIG. 4, since it is a portion that is superposed on the mounting plate portion 24 of the outer member 21, it is possible to ensure the strength by overlapping these two overhanging plate portions 27 and the mounting plate portion 24. it can.

  Further, as shown in FIG. 3, the overhanging plate portion 27 is not provided over the entire circumference, and only a position corresponding to the stopper rubber portion 3b is provided partially large, and thus functions as a stopper portion. While the strength of the portion is ensured by the above-described polymerization effect, other portions can be lightened by not providing the overhanging plate portion 27.

  As shown in FIGS. 1 to 4, the main rubber member 3 is formed from a rubber-like elastic material in a frustoconical cross-sectional shape around the axis O, and the outer peripheral surface of the boss member 1 a and the inner peripheral surface of the main body member 25. Vulcanized and bonded between the inner circumferential surface of the inner cylinder member 26 and the upper surface of the overhanging plate portion 27.

  Further, a rubber wall portion 3a vulcanized and bonded to the inner peripheral surface of the inner cylinder member 26 is connected to the lower end portion (lower end in FIG. 4) of the main body rubber portion 3, and the rubber wall portion 3a includes a figure. As shown in FIG. 2 and FIG. 4, a side surface of an intermediate rubber member 4 described later is in contact.

  Further, from the side surface of the main rubber member 3, a stopper rubber portion 3b which is vulcanized and bonded to the upper surface (upper side surface in FIG. 4) of the extended plate portion 27 is connected. When vibration of a large displacement in the direction (the vertical direction in FIG. 1) is input, the lower surface of the upper member 1 (flat plate member 1b) is brought into contact, and a stopper action is exhibited.

  As shown in FIGS. 2 and 4, the intermediate rubber member 4 is formed of a rubber-like elastic material and is formed in an annular shape symmetrical around the axis O, and is interposed between the main rubber member 3 and the bottom plate portion 22. It is arranged. The insertion member 5 is drilled along the axis O and includes an insertion hole 41 at the center. The insertion member 5 is inserted into the insertion hole 41.

  Between the engine side member EM and the outer member 21 (bottom plate portion 22), as shown in FIGS. 1 and 2, there is disposed a stopper member 7 made of a self-lubricating rubber-like elastic material in a disc shape. Thus, the generation of a hitting sound when the engine-side member EM collides with the bottom plate portion 22 due to a large displacement input is prevented.

  Note that the vibration isolator 100 has a gap t1 between the upper surface of the intermediate rubber member 4 and the lower surface of the main rubber member 3, as shown in FIG. The gap t2 is formed between the upper surface of the stopper rubber portion 3b and the lower surface of the upper member 1 (flat plate member 1b), and the gap t1 is configured to be smaller than the gap t2 (t1 < t2).

  As described above, the intermediate rubber member 4 is configured separately from the main body rubber member 3, and the intermediate rubber member 4 is disposed between the main body rubber member 3 and the bottom plate portion 22, and an engine (not shown). According to the vibration isolator 100, the gap t1 is formed between the upper surface of the intermediate rubber member 4 and the lower surface of the main rubber member 3. Since only the main rubber member 3 contributes to the support of the engine load and the intermediate rubber member 4 does not contribute, the dynamic spring constant in the hanging direction (vertical direction in FIG. 4) is reduced correspondingly to prevent idling input. The vibration effect can be improved.

  When a large displacement vibration exceeding the gap t1 is input to the vibration isolator 100 in the hanging direction (vertical direction in FIG. 4), the main rubber member 3 comes into contact with the intermediate rubber member 4, and these main bodies Both the rubber members 3 and 4 of the rubber member 3 and the intermediate rubber member 4 are deformed to receive an input of a large displacement.

  As a result, only the main rubber member 3 is contributed at the time of idling input, and the dynamic spring constant is reduced to ensure the vibration isolation effect, while the intermediate rubber is added to the main rubber member 3 at the time of large displacement vibration input. The contribution of the member 4 also makes it possible to suppress the amount of distortion of the main rubber member 3 and improve its durability.

  When a vibration exceeding the large displacement vibration described above is further input, the input of the large displacement is restricted by contacting the lower surface of the upper member 1 (flat plate member 1b) to the stopper rubber portion 3b. can do. As a result, the amount of distortion of the main rubber member 3 and the intermediate rubber member 4 can be suppressed, and the durability can be improved.

  Moreover, according to the vibration isolator 100 in this Embodiment, while the intermediate rubber member 4 is provided with the insertion hole 41 for inserting the insertion member 5 so that it may mention later, this intermediate rubber member 4 is attached to the outer member 21. Since the intermediate rubber member 4 is located in the space formed on the upper surface of the bottom plate portion 22, that is, on the inner peripheral side of the outer cylinder portion 23 of the outer member 21 (that is, the inner peripheral side of the rubber wall portion 3 a). When the insertion member 5 is displaced in the lateral direction, the intermediate rubber member 4 (and the rubber wall portion 3a) can be pressed between the insertion member 5 and the inner peripheral side of the outer cylinder portion 23.

  That is, when the insertion member 5 is displaced in the lateral direction (left-right direction in FIG. 4) with the displacement of the engine at the time of acceleration input, not only the displacement of the insertion member 5 is received by the main rubber member 3, but also in the middle Since the rubber member 4 can also receive the displacement of the insertion member 5, the thickness dimension in the displacement direction can be increased by the amount corresponding to the intermediate rubber member 4 to avoid a sudden increase in the dynamic spring constant. it can.

  As a result, as described above, only the main rubber member 3 contributes to reduce the dynamic spring constant at the time of idling input, while ensuring the anti-vibration effect, while adding to the main rubber member 3 at the time of acceleration input. The intermediate rubber member 4 is also contributed to ensure the thickness dimension of the rubber member in the lateral direction, thereby suppressing a sudden increase in the dynamic spring constant due to the displacement in the lateral direction. Generation of sound can be suppressed.

  Next, the detailed configuration of the outer member 21 will be described with reference to FIG. 5A is a top view of the outer member 21, and FIG. 5B is a cross-sectional view of the outer member 21 taken along the line Vb-Vb in FIG. 5A.

  As described above, the external member 21 is a member that constitutes the base member 2 together with the main body member 25, and includes a bottom plate portion 22, an inner cylinder portion 23, and a mounting plate portion 24 as shown in FIG. In addition, the bottom plate portion 22 has an opening 22a.

  As described above, the opening 22a is a part through which the insertion member 5 is inserted, and as shown in FIG. 5A, the opening 22a has an oval shape that is long in the longitudinal direction of the outer member 21 (attaching plate portion 24). Is formed. The major axis L direction (left and right direction in FIG. 5A) of the opening 22a is located along the displacement direction of the insertion member 5 at the time of acceleration input.

  Next, the detailed configuration of the intermediate rubber member 4 will be described with reference to FIGS. 6 and 7. FIG. 6A is a top view of the intermediate rubber member 4, and FIG. 6B is a bottom view of the intermediate rubber member 4. FIG. 7 is a cross-sectional view of the intermediate rubber member 4 taken along line VII-VII in FIG.

  As described above, the intermediate rubber member 4 is formed from a rubber-like elastic material in an annular shape symmetrical around the axis O, and is formed in the center as shown in FIGS. By inserting slits 4 at four locations from the outer edge toward the axis O, the insertion holes 41, the lip part 43 projecting outward from the outer edge of the seat surface 42 abutting against the bottom plate part 22, It is mainly configured by four divided body portions 45 formed between the slits and a sandwiched portion 46 protruding from the seating surface 42.

  As described above, the insertion hole 41 is a portion through which the insertion member 5 is inserted (see FIG. 2), and has a circular cross section symmetric about the axis O and has an inner diameter slightly larger than the outer diameter of the insertion member 5. Is formed. The seat surface 42 is a flat surface that is in contact with the bottom plate portion 22 and has an outer diameter larger than the dimension in the major axis L direction (the size in the left-right direction in FIG. 6A) of the opening 22a that is opened in the bottom plate portion 22. It is formed in a circle.

  As will be described later, the lip portion 43 serves as a guide when the intermediate rubber member 4 moves in the left-right direction (left-right direction in FIG. 7), and is formed in a flange shape that projects outward. The seat surface 42 and the lower surface of the lip 43 (the lower side surface in FIG. 7) are formed flush with each other as shown in FIGS.

  Here, the function of the lip portion 43 will be described with reference to FIGS. 8 and 9. FIG. 8 is a partially enlarged cross-sectional view of the vibration isolator 100, and FIG. 9 is a partially enlarged cross-sectional view of the vibration isolator when the lip portion 43 of the intermediate rubber member 4 is omitted.

  8A and 9A correspond to the state where the insertion member 5 is in the initial position, and FIGS. 8B and 9B show the insertion member 5 in the lateral direction from the initial position. Corresponds to the state moved to. Moreover, the difference between the vibration isolator 100 shown in FIG. 8 and the vibration isolator shown in FIG. 9 is only the presence or absence of the lip portion 43, and the other parts are all configured identically.

  Assuming that the intermediate rubber member 4 is configured without the lip portion 43 as shown in FIG. That is, as the insertion member 5 is displaced in the lateral direction (left direction in FIG. 9A) during acceleration input, the intermediate rubber member is moved in the same direction as the displacement of the insertion member 5 as shown in FIG. 9A. When the intermediate rubber member 4 is about to return from the moving direction to the opposite direction (the right direction in FIG. 9A) after the movement, the return direction as shown in FIG. 9B. The outer edge on the side (the side surface on the right side in FIG. 9) fits into the opening 22a of the bottom plate 22 and cannot return to the initial position, or the portion fitted into the opening 22a is damaged.

  On the other hand, according to the vibration isolator 100 in the present embodiment, since the lip portion 43 protruding outward from the outer edge of the seating surface 42 is provided in the intermediate rubber member 4, the side of the insertion member 5 at the time of acceleration input is provided. As shown in FIG. 8 (a), the intermediate rubber member 4 is moved in the direction of displacement of the insertion member 5 in accordance with the displacement in the direction (the left direction in FIG. 8 (a)), and then reverse from the moving direction. When the intermediate rubber member 5 is about to return in the direction (right side in FIG. 8 (a)), as shown in FIG. 8 (b), the lip portion 43 serves as a guide, so that the return direction side It is possible to avoid that the outer edge (right side in FIG. 8) fits into the opening 22 a of the bottom plate portion 22.

  Moreover, according to the vibration isolator 100 in this Embodiment, as shown to Fig.8 (a), the upper surface of the baseplate part 22 of the outer member 21, the inner cylinder member 25 of the main body member 25, and the rubber | gum of the main body rubber member 3 are used. A gap t3 is formed between the lower surface of the wall 3a and the lip portion 43 is positioned in the space formed by the gap t3 in the initial state (the state in which there is no lateral movement). Therefore, it is possible to effectively use a useless space that becomes a dead space.

  Thereby, by providing the lip portion 43, the outer diameter of the intermediate rubber member 4 as a whole is reduced, and the disadvantage that the durability is lowered, or the volume (outer diameter) of the intermediate rubber member 4 is ensured. Therefore, it is possible to avoid a problem that the vibration isolator 100 as a whole is increased in size as the diameter of the base member 2 (the inner cylinder portion 26 and the outer cylinder portion 23) is increased. That is, while reducing the size of the vibration isolator 100 as a whole, it is possible to secure the volume of the intermediate rubber member 4 and efficiently improve the durability and suppress the booming noise during acceleration input.

  Returning to FIG. 6 and FIG. As shown in FIGS. 6 and 7, the slit 44 is a notch extending from the outer edge of the intermediate rubber member 4 toward the center (axis O), and the slit 44 is formed at four locations in the circumferential direction. By being formed at a predetermined interval, as shown in FIG. 6, four divided body portions 45 are formed between these slits 44.

  As shown in FIG. 6, the four divided body portions 45 include a pair of first divided body portions 45 a positioned on the long axis L of the opening 22 a and a pair of holes positioned across the long axis L of the opening 22 a. The second divided body portion 45b is configured (see FIG. 9), and the width of the first divided body portion 45a is shorter than the width of the second divided body portion 45b (that is, the first divided body portion). The angle θ1 between the slits 44 forming the part 45a is set to be smaller than the angle θ2 between the slits 44 forming the second divided body part 45b (θ1 <θ2)).

  Here, the function of the slit 44 will be described with reference to FIGS. 10 and 11. FIG. 10 is a bottom view of the vibration isolator 100. Also. FIG. 11A is a partially enlarged cross-sectional view of the vibration isolator 100, and FIG. 11B is a partially enlarged cross-sectional view of the vibration isolator when the slits 44 of the intermediate rubber member 4 are omitted. is there.

  10 corresponds to the state in which the vibration isolator 100 in FIG. 3 is viewed from the back side of the drawing. FIGS. 11A and 11B show that the insertion member 5 is moved laterally from the initial position. Corresponds to the state. Moreover, the difference between the vibration isolator 100 shown in FIG. 11A and the vibration isolator shown in FIG. 11B is only the presence or absence of the slit 44, and all other parts are configured identically.

  As described above, the opening 22a opened in the bottom plate portion 22 of the outer member 21 has, as shown in FIG. 10, the major axis L direction (the left-right direction in FIG. 10) is the displacement direction (that is, the insertion) during acceleration input. The seating surface 42 of the intermediate rubber member 5 that is formed in an oval shape that is a moving direction of the member 5 and is in contact with the bottom plate portion 22 has a dimension in the major axis L direction of the opening 22a (dimension in the left-right direction in FIG. 10). It is formed in a larger-diameter circle.

  This increases the contact area between the seating surface 42 of the intermediate rubber member 5 and the bottom plate portion 22 while ensuring a displaceable region of the insertion member 5, thereby improving the durability of the intermediate rubber member 5 and preventing it. The size of the vibration device 100 as a whole can be reduced.

  That is, when the contact area between the seating surface 42 of the intermediate rubber member 4 and the bottom plate portion 22 cannot be ensured, the intermediate rubber member is input when a large displacement is input in the suspending direction (front side in FIG. 10). While the displacement (strain amount) of 4 increases and its durability is lowered, when the contact area between the seat surface 42 of the intermediate rubber member 4 and the bottom plate portion 22 is widened, the durability is improved. However, there is a problem that the vibration isolator 100 as a whole is increased in size. Further, when the opening area of the opening 22a is reduced, it is possible to obtain an increase in size and a contact area, but it is not possible to secure a region necessary for the movement of the insertion member 5. There is.

  On the other hand, according to the vibration isolator 100 in the present embodiment, the opening 22a is formed in an oval shape in which the long axis L direction is the moving direction of the insertion member at the time of acceleration input. The area of the opening 22a can be further reduced while securing the necessary area.

  Since the opening 22a is formed in an oval shape in this way, the seating surface 42 of the intermediate rubber member 4 is formed in a circle, so that the intermediate rubber member 4 can be reduced in size while the seat of the intermediate rubber member 4 is seated. The contact area between the surface 42 and the bottom plate portion 22 can be efficiently ensured as much as necessary. As a result, the above-described problems can be solved.

  Here, according to the vibration isolator 100 in the present embodiment, as described above, when the insertion member 5 is displaced laterally during acceleration input, the lip portion 43 serves as a guide, so The outer edge of the rubber member 4 is prevented from entering the opening 22a (see FIG. 8).

  However, when the displacement at the time of acceleration input is large, as shown in FIG. 11, not only the lip portion 43 is separated from the inner edge of the opening 22a but also the eccentric deformation of the intermediate rubber member 4 is large. As shown in (b), the lip portion 43 is inclined and wrinkled, so that the lip portion cannot sufficiently exhibit the role of the guide.

  On the other hand, according to the vibration isolator 100 in the present embodiment, the slits 44 are extended from the outer edge of the intermediate rubber member 4 toward the central portion at four locations, and four divided body portions are provided between the slits 44. 45, that is, the lip portion 43 is divided at four locations, so that the displacement at the time of acceleration input is large, and the intermediate rubber member 4 is greatly deformed eccentrically as the insertion member 5 moves in the lateral direction. Even when the lip portion 43 is not continuous, the lip portion 43 is not continuous in the circumferential direction, and as shown in FIG. Thus, the lip portion 43 can sufficiently exert its role as a guide.

  In addition, as described above, the slit 44 does not divide only the lip portion 43 but extends to a position beyond the lip portion 43 (four divided body portions 45 are formed). When the member 4 is greatly eccentrically deformed, it is possible not only to prevent the lip portion 43 from being inclined and wrinkles but also to suppress the deformation of the intermediate rubber member 4 itself.

  In particular, it is difficult for the deformation of the part on the eccentric direction side to affect the part on the opposite side to the eccentric direction, so that the part on the opposite side to the eccentric direction (particularly, the divided body portion 45a) maintains the initial shape. Can do. As a result, as shown in FIG. 11 (a), it is possible to effectively suppress the inclination and wrinkle of the lip 43 caused by the eccentric deformation, and to make the lip 43 function more reliably as a guide. Can do.

  Here, as shown in FIG. 10, since the opening 22a is formed in an oval shape, the intermediate rubber member 4 is greatly eccentrically deformed in the long axis L direction (left-right direction in FIG. 10) of the opening 22a. However, as described above, the four divided body portions 45 formed between the slits 44 have the width dimension (angle θ1) of the pair of first divided body portions 45a located on the long axis of the opening 22a. It is made shorter than the width dimension (angle (theta) 2) of a pair of 2nd division body part 45b located on both sides of the major axis L of the opening part 22a (refer to Fig.6 (a) made into the small angle).

  Thereby, even when the intermediate rubber member 4 is greatly eccentrically deformed in the major axis L direction of the opening 22a, the above-described operation for maintaining the initial shape in the portion opposite to the eccentric direction is more effectively performed. As a result, as shown in FIG. 11 (a), the lip 43 can be effectively restrained from tilting and wrinkling due to eccentric deformation, and the lip 43 can serve as a guide. It can be demonstrated more reliably.

  In addition, here, when the lower surface of the main rubber member 3 comes into contact with and presses the upper surface of the intermediate rubber member 4 in accordance with the input of a large displacement vibration in the hanging direction (for example, the lower direction in FIG. 4), The air left between the rubber members 3 and 4 is compressed, and the compressed air is discharged to the outside at once from the contact surface between the main rubber member 3 and the intermediate rubber member 4. An abnormal noise occurs.

  In contrast, in the vibration isolator 100 according to the present embodiment, as shown in FIG. 10, the slit 44 extends to a position reaching the opening 22 a of the bottom plate portion 22. It is possible to secure a path for the air left between the members 3 and 4 to escape from the opening 22a to the outside. As a result, it is possible to prevent the air from being compressed and to suppress the generation of abnormal noise.

  Returning to FIG. 6 and FIG. The sandwiched portion 46 is located between the insertion member 5 and the inner edge of the opening 22a, and is a part for preventing a hitting sound when the insertion member 5 collides with the inner edge of the opening 22a. As shown to b), it is formed in the ellipse shape corresponding to the shape of the opening part 22a.

  Thus, when a large displacement is input in the lateral direction, the sandwiched portion 46 is sandwiched between the insertion member 5 and the inner edge of the opening 22a, so that the insertion member 5 directly collides with the inner edge of the opening 22a. In addition to preventing this, the impact at the time of collision can be absorbed by the sandwiched portion 46 to suppress the occurrence of hitting sound.

  Furthermore, since the sandwiched portion 46 is configured to be positioned away from the inner edge of the opening 22a (see FIG. 10), when the insertion member 5 collides with the inner edge of the opening 22a, the collision Along with this, the sandwiched portion 46 rides on the upper surface (for example, the upper side surface of FIG. 4) of the bottom plate portion 22 from the opening portion 22a, and enters the opening portion 22a while the sandwiched portion 46 rides on the upper surface of the bottom plate portion 22. It is possible to suppress the inconvenience of not returning, and as a result, it is possible to suppress the sandwiched portion 46 from being cut and to stably exhibit the above-described effect of suppressing the hitting sound.

  Next, a second embodiment will be described with reference to FIG. FIG. 12A is a top view of the intermediate rubber member 204 in the second embodiment, and FIG. 12B is a cross-sectional view of the intermediate rubber member 204 taken along line XII-XII in FIG. .

  In the first embodiment, the case where the slit 44 is extended in the intermediate rubber member 4 has been described. However, in the second embodiment, the extension of the slit 44 is omitted. In addition, the same code | symbol is attached | subjected to the part same as 1st Embodiment mentioned above, and the description is abbreviate | omitted.

  As shown in FIG. 12, the intermediate rubber member 204 in the second embodiment is formed in a symmetric annular shape around the axis O from the rubber-like elastic material, and a lip portion protruding outward from the outer edge of the seating surface 42. 243 and a concave groove 244 provided in the upper surface are mainly provided.

  The lip part 243 is a part that plays the role of a guide when the intermediate rubber member 204 moves in the left-right direction (FIG. 12B, left-right direction), like the lip part 43 in the first embodiment described above. In the second embodiment, it is formed over the entire circumference of the outer edge of the intermediate rubber member 204 as shown in FIG. 12 (a). The seat surface 42 and the lower surface of the lip portion 243 (the lower surface in FIG. 12B) are formed flush with each other as shown in FIG.

  The concave groove 244 is a part that functions as an exhaust passage for preventing the generation of noise by letting air between the main rubber member 3 and the intermediate rubber member 204 to the outside when a large displacement is input. As shown in FIG. 12 (a), eight are arranged in a radial line shape at equal intervals in the circumferential direction (45 degree intervals) with the axis O as the center.

  The cross-sectional shape along the extending direction of the recessed groove 244 is recessed according to the shape of the upper surface of the intermediate rubber member 204. As shown in FIG. The remaining portion is recessed so as to be inclined downward so as to approach the seating surface 42 toward the outer edge side. In addition, in the outermost edge part, as shown in FIG.12 (b), it is recessedly provided substantially parallel to the seat surface 42. As shown in FIG.

  Thereby, even when the lower surface of the main rubber member 3 comes into contact with the upper surface of the intermediate rubber member 204 and presses it with the input of the vibration of a large displacement in the hanging direction (for example, the lower direction in FIG. 4), Since the air left between the rubber members 3 and 204 can be discharged from the concave grooves 204 to the outside through the insertion holes 41 and the openings 22a, the air is prevented from being compressed in advance. Thus, the generation of abnormal noise can be suppressed.

  Next, a third embodiment will be described with reference to FIG. FIG. 13A is a top view of the intermediate rubber member 304 in the third embodiment, and FIG. 13B is a cross-sectional view of the intermediate rubber member 304 taken along line XIII-XIII in FIG. .

  In the first embodiment, the case where the slit 44 is extended in the intermediate rubber member 4 has been described. However, in the second embodiment, the extension of the slit 44 is omitted. In addition, the same code | symbol is attached | subjected to the part same as each above-mentioned embodiment, and the description is abbreviate | omitted.

  As shown in FIG. 13, the intermediate rubber member 304 in the third embodiment is formed from a rubber-like elastic material in a symmetrical annular shape around the axis O, and has protrusions 344a and 344b protruding from the upper surface. It is configured to prepare for.

  The protrusions 344a and 344b are parts for securing an exhaust passage that allows the air between the main rubber member 3 and the intermediate rubber member 304 to escape to the outside in order to suppress the generation of abnormal noise when a large displacement is input. As shown in FIG. 13A, eight protrusions 344a are arranged at equal intervals in the circumferential direction (45 degree intervals) on the outer edge side, and the protrusions 344b are arranged at equal intervals in the circumferential direction (45 degrees on the axis O side). 8 are arranged in the (interval).

  The protrusion 344a is disposed so as to be displaced by 22.5 degrees in the circumferential direction with respect to the protrusion 344b. In addition, the protrusions 344a and 344b are configured as spherical protrusions, and the protrusion 344a has a larger diameter than the protrusion 344b (approximately four times in this embodiment).

  Thereby, even when the lower surface of the main rubber member 3 comes into contact with and presses the upper surface of the intermediate rubber member 304 in accordance with the input of the large displacement vibration in the hanging direction (for example, the lower direction in FIG. 4), A gap is formed between the contact surfaces by the height of the protrusions 344a and 344b, and the air left between the rubber members 3 and 304 can be discharged to the outside through the insertion hole 41 and the opening 22a. Therefore, it is possible to prevent the air from being compressed and to suppress the generation of abnormal noise.

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

  For example, the numerical values given in the above embodiments are merely examples, and other numerical values can naturally be adopted.

  In the second and third embodiments, the lip portion 243 is formed continuously in the circumferential direction. In this case, it is preferable that the part of the division is the same as that in the first embodiment.

  In the second embodiment, the case where the concave groove 244 is provided in the upper surface of the intermediate rubber member 204 has been described. However, the present invention is not limited to this. For example, a ridge is radiated on the upper surface of the intermediate rubber member 204. It may be extended linearly.

It is a front view of the vibration isolator in 1st Embodiment of this invention. It is a fragmentary sectional perspective view of a vibration isolator. It is a top view of a vibration isolator. It is sectional drawing of the vibration isolator in the IV-IV line of FIG. (A) is a top view of an outer member, (b) is sectional drawing of the outer member in the Vb-Vb line | wire of Fig.5 (a). (A) is a top view of an intermediate rubber member, (b) is a bottom view of the intermediate rubber member. It is sectional drawing of the intermediate | middle rubber member in the VII-VII line of Fig.6 (a). It is a partial expanded sectional view of a vibration isolator. It is a partial expanded sectional view of a vibration isolator in the case where a lip portion of an intermediate rubber member is omitted. It is a bottom view of a vibration isolator. (A) is the elements on larger scale of the vibration isolator in this Embodiment, (b) is the elements on larger scale of the vibration isolator in the case where the slit of the intermediate rubber member is omitted. (A) is a top view of the intermediate rubber member in 2nd Embodiment, (b) is sectional drawing of the intermediate rubber member 4 in the XII-XII line | wire of Fig.12 (a). (A) is a top view of the intermediate rubber member in 3rd Embodiment, (b) is sectional drawing of the intermediate rubber member in the XIII-XIII line | wire of Fig.13 (a). It is sectional drawing of the conventional suspension type vibration isolator.

Explanation of symbols

100 Vibration isolator 1 Upper member 1a Boss member (part of upper member)
1b Flat plate member (part of upper member)
2 Base member 21 External material 22 Bottom plate portion 22a Opening portion 23 Outer tube portion 24 Mounting plate portion 25 Main body member 26 Inner tube portion 27 Overhang plate portion 3 Main body rubber member 3a Rubber wall portion 3b Stopper rubber portion 4 Intermediate rubber member 41 Insertion hole 42 Seat surface 43 Lip part 44 Slit 45 Divided body part 45a First divided body part 45b Second divided body part 46 Clamping part 5 Inserting member t1 Clearance (first gap)
t2 gap (second gap)
t3 gap (third gap)
L Long axis O Center axis BF Body frame EM Engine side member

Claims (5)

An upper member, a base member having an opening, a main rubber member configured to connect the upper member and the base member and made of a rubber-like elastic material, and attach the base member to the vehicle body frame side In the vibration isolator for supporting the engine suspended from the vehicle body frame by connecting one end of the insertion member inserted through the opening of the base member to the upper member and connecting the other end to the engine side. ,
An intermediate rubber member that is disposed between the main rubber member and the base member and is made of a rubber-like elastic material, and is disposed on the upper surface of the base member and contacts the lower surface of the upper member when a large displacement is input. With a stopper rubber part that comes into contact,
The base member is
A bottom plate portion in which the opening is formed; a cylindrical outer cylinder portion that rises from the bottom plate portion; and an attachment plate portion that projects outward from the upper end of the outer cylinder portion and is attached to the vehicle body frame side. An outer member having
A cylindrical inner cylinder portion having an outer diameter corresponding to the inner diameter of the outer cylinder portion of the outer member, and an overhang that projects outward from the upper end of the inner cylinder portion and is superimposed on the attachment plate portion of the outer member And a main body member to which the main body rubber member is coupled,
The outer member and the main body member are configured integrally by the inner tube portion of the main body member being press-fitted into the outer tube portion of the outer member,
The stopper rubber portion is connected to the upper surface of the overhang plate portion of the main body member, and is configured integrally with the main body rubber member,
The intermediate rubber member includes an insertion hole through which the insertion member is inserted, and is disposed on the upper surface of the bottom plate portion of the outer member,
In a state where the engine is suspended and supported with respect to the body frame, a first gap is formed between the upper surface of the intermediate rubber member and the lower surface of the main rubber member, and the first gap is An anti-vibration device configured to be smaller than a second gap formed between a stopper rubber portion and a lower surface of the upper member. A third gap is formed between the upper surface of the bottom plate portion of the outer member and the lower surface of the main body member or the main body rubber member,
The intermediate rubber member includes a lip portion projecting outward from an outer edge of a seating surface that is in contact with the bottom plate portion, and the lip portion is located in the third gap. Item 1. A vibration isolator according to item 1. The opening portion opened in the bottom plate portion is formed in an oval shape, and the long axis direction of the oval shape is located along the displacement direction at the time of acceleration input,
The intermediate rubber member has a seat surface that is in contact with the bottom plate portion formed in a circular shape having an outer diameter larger than the dimension in the major axis direction of the opening, and slits at four locations from the outer edge toward the center portion. It is provided with four divided parts formed between each slit by extending,
The four divided body parts are composed of a pair of first divided body parts located on the long axis of the opening and a pair of second divided body parts located across the long axis of the opening. The vibration isolator according to claim 2, wherein a width dimension of the first divided body part is shorter than a width dimension of the second divided body part.   The vibration isolator according to claim 3, wherein the slit extends to a position reaching the opening of the bottom plate.   The intermediate rubber portion includes a sandwiched portion that protrudes from the seat surface and is sandwiched between the insertion member and the opening when a large displacement is input, and the sandwiched portion extends from an inner edge of the opening. The vibration isolator according to any one of claims 1 to 4, wherein the vibration isolator is spaced apart.

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