JP4667436B2 - Liquid-filled vibration isolator - Google Patents

Description

  The present invention relates to a liquid-sealed vibration isolator, and in particular, a liquid-sealed liquid that can reduce the size of a driving device while reliably switching the communication state between a main liquid chamber and a sub liquid chamber. The present invention relates to a type vibration isolator.

  As a liquid-filled vibration-proof device, a liquid-filled chamber is formed between the vibration-proof substrate and the diaphragm, and the liquid-filled chamber is divided into a main liquid chamber and a sub-liquid chamber by a partition body, and an orifice provided in the partition body In some cases, the main liquid chamber and the sub liquid chamber communicate with each other. This type of liquid-filled vibration isolator is, for example, disposed between an automobile engine and a vehicle body frame, and attenuates engine vibrations by the fluid flow effect of the liquid flowing between the two liquid chambers via an orifice. Thus, vibration is prevented from being transmitted to the vehicle body frame.

  In recent years, a switchable liquid-filled vibration isolator having a plurality of (for example, two) orifices and switching means for switching the communication state between the main liquid chamber and the sub liquid chamber by the orifices has been proposed. Has been.

For example, Patent Document 1 discloses a switching chamber capable of selectively introducing atmospheric pressure and negative pressure, and a first diaphragm that forms a second liquid chamber (sub liquid chamber) between a partition member (partition body) and And an urging member that presses the first diaphragm against the partition member to close the inner orifice (one of the first and second orifices), introduces negative pressure into the switching chamber, and attaches the first diaphragm. A technique for opening the inner orifice by disengaging the biasing member from the partition member against the biasing of the biasing member is disclosed. Thereby, the communication state between both liquid chambers can be switched by the switching means, and vibration can be reduced in a wide frequency band (Patent Document 1).
WO2003 / 008838

  By the way, in the above-described conventional liquid-filled vibration isolator, when the first diaphragm is pushed back by the hydraulic pressure at the time of vibration input in a state in which the inner orifice is closed, the inner orifice is opened and desired characteristics (fluid flow (Effect) cannot be obtained. Therefore, it is necessary to increase the spring constant of the urging member and firmly press the first diaphragm against the partition member.

  However, when opening the inner orifice, it is necessary to disengage the first diaphragm from the partition member against the urging force of the urging member. Therefore, if the urging member has a high spring constant, it is introduced into the switching chamber. It is necessary to reduce the negative pressure to a lower pressure. Therefore, in order to perform switching reliably, a drive device with a larger output is required, and there is a problem that the drive device is increased in size accordingly.

  The present invention has been made to solve the above-described problems, and is a liquid that can reduce the size of the drive device while reliably switching the communication state between the main liquid chamber and the sub liquid chamber. An object of the present invention is to provide an enclosed vibration isolator.

In order to achieve this object, a liquid-filled vibration isolator according to claim 1 connects a first fixture, a cylindrical second fixture, the second fixture, and the first fixture. And a vibration isolating base composed of a rubber-like elastic body, a diaphragm attached to the second fixture to form a liquid sealing chamber between the anti-vibration base, and the liquid sealing chamber as the vibration isolating base. A partition that partitions the main liquid chamber on the side and the sub liquid chamber on the diaphragm side, a first orifice and a second orifice that are formed in the partition and communicate with each other, and the diaphragm Is pressed against the partition to close the first orifice, and the diaphragm is detached from the partition to open the first orifice, thereby establishing a communication state between the main liquid chamber and the sub liquid chamber. Switching means for switching The switching means includes a driving device having a rotating shaft and rotationally driving the rotating shaft, and a rotating male screw portion fixed to the rotating shaft of the driving device and having a screw formed on the outer peripheral surface thereof. And a linearly-moving female screw part formed on an inner peripheral surface of a female screw that can be screwed to the male screw of the male screw part, and a guide part that guides the linearly-moving female screw part in the axial direction of the screw. The drive device rotates the rotation shaft to rotate the rotation male screw portion at a fixed position, and gives the rotation to the linear motion female screw portion. The guide part is configured to be movable in the axial direction of the screw, and the linearly-moving female screw part has a pressing surface that is formed in a flat surface on one end side in the axial direction of the screw and can press the diaphragm. Comprising rotating the rotating male threaded part in the forward rotation direction or the reverse rotation direction, By moving the moving screw portion in the direction approaching the partition body, the diaphragm is pressed against the partition body by the pressing surface of the linear motion screw portion to close the first orifice, and the rotation By rotating the male screw portion in the reverse rotation direction or the forward rotation direction and moving the linearly moving female screw portion in a direction away from the partition body, the diaphragm is detached from the partition body, and the first The orifice is opened, and the drive device includes a case portion that forms an outer shape, and the guide portion is configured as a guide groove that is recessed in the outer peripheral surface of the case portion and extends along the axial direction of the screw, The linearly-moving female screw portion includes a cylindrical main body portion in which the female screw is formed on an inner peripheral surface and the pressing surface is formed on one end side in the axial direction of the screw, and an axial direction of the screw of the main body portion. The other end A plate-like projecting wall projecting outward along the upper surface of the case part from the side, and an engaging claw extending from the projecting wall toward the case part and engaged with the guide groove with Ru.

The claim 2 hydraulic antivibration device according, the hydraulic antivibration device according to claim 1 Symbol placement, the linear internal thread portion is provided with a convex portion that is projectingly provided from the pressing surface, The diaphragm includes a recessed portion that is recessed in a pressed surface that is pressed against the pressing surface of the linearly-moving female screw portion, and that receives the protruding portion, and the opening of the recessed portion of the diaphragm is the linear motion It is configured to have a larger diameter than the outer diameter of the projecting portion of the female thread portion, and the bottom portion is configured to have a smaller diameter than the opening portion, thereby including an inclined surface that is inclined from the opening portion toward the bottom portion, When the pressing surface of the linear motion female screw portion presses the diaphragm against the partition body, the convex portion of the linear motion female screw portion is guided to the bottom by the inclined surface of the concave portion.

  According to the liquid-filled vibration isolator according to claim 1, the main liquid chamber and the sub liquid chamber are communicated with each other, and the first orifice, the second orifice, and the diaphragm are pressed against the partition body to close the first orifice. And a switching means for switching the communication state between the main liquid chamber and the sub liquid chamber by opening the first orifice by detaching the diaphragm from the partition body, and when vibration is input, By switching the communication state between the two liquid chambers according to the switching means, vibrations in different frequency bands can be applied to the first orifice and / or the second orifice, and as a result, vibrations in a wide frequency band. Can be reduced.

  Here, according to the present invention, the switching means includes a driving device that has a rotating shaft and rotationally drives the rotating shaft, and a rotating male screw portion that is fixed to the rotating shaft of the driving device and has a screw formed on the outer peripheral surface thereof. And a drive unit that includes a linearly-moving internal threaded portion in which a female thread that can be screwed to the external thread of the external threaded portion is formed on the inner peripheral surface, and a guide portion that guides the linearly-movable internal threaded portion in the axial direction of the screw. By rotating the rotating shaft and rotating the rotating male screw portion at a fixed position, the screw of the rotating male screw portion and the female screw of the direct acting female screw portion are screwed into the direct acting female screw portion. The rotation can be given, and the linearly-moving internal thread portion to which the rotation is given can be moved in the axial direction of the screw by the guide of the guide portion.

  The linearly-moving internal thread portion is provided with a pressing surface that is formed in a flat surface on one end side in the axial direction of the screw and can press the diaphragm. Therefore, the rotating external thread portion is rotated in the forward rotation direction or the reverse rotation direction. By moving the moving screw portion in the direction approaching the partition body, the diaphragm is pressed against the partition body by the pressing surface of the linear motion screw portion to close the first orifice and reverse the rotating male thread portion. The diaphragm is detached from the partition body and the first orifice can be opened by rotating in the rotation direction or the rotation direction in the normal rotation direction and moving the linearly-moving female screw portion in a direction away from the partition body.

  That is, according to the present invention, the rotational motion of the drive device (rotating male screw portion) is converted into the linear motion (linear motion) of the linear motion female screw portion, and the diaphragm is partitioned by the pressing surface of the linear motion female screw portion. Since the structure is such that the diaphragm is removed from the partition body by retreating the linearly-moving female screw portion while being pressed against the body, an urging member (elastic spring) is provided for pressing the diaphragm against the partition body as in the conventional product. There is no need. Therefore, unlike the conventional product, there is no need to separate the diaphragm from the partition body against the biasing of the biasing member, so that the necessary driving force can be suppressed and the driving device can be reduced in size accordingly. There is an effect.

  Further, as described above, according to the present invention, since the screw engagement between the rotating male screw portion and the linearly-moving female screw portion is used, the rotational motion is converted into the linearly-moving motion, and the linearly-moving female screw is converted. In addition to moving the part in the axial direction of the screw (advancing and retreating), the wedge force of the screw can be used to exert that force as a pressing force, so the drive device is small (output) Even if it is small, there is an effect that the diaphragm can be firmly pressed to the partition body by the pressing surface of the linearly-moving female screw portion.

  As a result, even when a force for pushing back the diaphragm from the partition body is generated by the hydraulic pressure at the time of vibration input, the diaphragm can be firmly pressed against the partition body and the state where the first orifice is closed can be reliably maintained. it can. That is, according to the present invention, it is possible to prevent the diaphragm from being pushed back due to the hydraulic pressure at the time of vibration input and the first orifice is inadvertently opened, so that desired characteristics (fluid flow effect) can be obtained. There is an effect that it can be surely exhibited.

  The shake region is a region where a large amplitude vibration is inputted and the hydraulic pressure becomes high. For example, when the first orifice is opened during idling and the first orifice is closed in the shake region, the first orifice is used. The configuration of the present invention that can reliably maintain the closed state of the orifice 21 is particularly effective.

  In addition, since the linearly-moving internal thread portion is configured such that rotation is restricted by the guide portion and only linear motion is allowed, as described above, the rotational motion is converted into linear motion, and the wedge effect of the screw is used. Therefore, there is an effect that it is possible to avoid twisting of the diaphragm pressed by the linearly-moving female screw portion, while ensuring a high pressing force.

  As a result, a wrinkle is formed in the diaphragm, leading to a decrease in durability thereof, and a gap is formed by the amount of wrinkle when pressed against the partition, so that the first orifice can be reliably closed. Therefore, there is an effect that it is possible to suppress a problem that desired dynamic characteristics cannot be obtained.

  Moreover, in the conventional product, the spring constant of the urging member (elastic spring) decreases due to aging deterioration due to use, and there is a possibility that the diaphragm cannot be firmly pressed against the partition body. According to the present invention, since the screw thread engagement between the rotary male screw portion and the linearly-moving female screw portion is used, the pressing force for pressing the diaphragm against the partition body can be stably exhibited over a long period of time. There is an effect.

  Here, contrary to the present invention, the switching means can be configured to rotate the female screw side at the fixed position and move the male screw side directly, but rotating the female screw at the fixed position The bearing structure and drive structure become complicated, leading to increased component and manufacturing costs and reduced reliability.

  On the other hand, according to the present invention, the male screw side (rotating male screw portion) is rotated at the fixed position, and the female screw side (linear moving female screw portion) is moved directly. This simplifies the structure for rotating at the same time, thereby reducing the component cost and manufacturing cost and improving the reliability.

  In addition, according to the present invention, when the rotational movement of the external thread (rotating external thread part) is converted into the rectilinear motion of the internal thread (directly moving internal thread part) by using the screwing of the external thread and the internal thread. Since the structure is such that the diaphragm is pressed by providing a pressing surface on one end side of the female screw (linear moving screw portion) that moves linearly, the two members of the member that linearly moves and the member that presses the diaphragm are moved linearly. It can also be used as a screw part.

  Therefore, it is not necessary to provide a separate mechanism for transmitting the linear motion between the member that linearly moves and the member that presses the diaphragm 9, so that the number of parts can be reduced. The manufacturing cost can be reduced, and the liquid-filled vibration isolator as a whole can be reduced in size.

Further, according to the present invention, includes a drive device casing portion constituting the outer shape, the configuration of the guide groove extending along the axial direction of the recessed on the outer peripheral surface of the case portion screw and the guide portion, the driving The case part can also be used as a member for housing the component parts (such as an electric motor) of the apparatus and a member for guiding the linearly-moving female screw part (which guides the axial direction of the screw while restricting rotation). Can do. Therefore, the number of parts can be reduced, and the parts cost and manufacturing cost can be reduced accordingly, and the liquid-filled vibration isolator as a whole can be reduced in size.

  Further, according to the present invention, the linearly-moving internal thread portion includes a cylindrical main body portion in which a female screw is formed on the inner peripheral surface and a pressing surface is formed on one end side in the axial direction of the screw, and the main body portion A plate-like projecting wall projecting outward from the other axial end of the screw along the upper surface of the case part, and an engaging claw extending from the projecting wall toward the case part. Since the engaging claw is engaged with the guide groove, a space is provided on the outer peripheral side of the main body (between the partition body and the overhanging wall) while allowing the linearly-moving female screw to be guided in the axial direction of the screw. There is an effect that it can be sufficiently formed. That is, by effectively utilizing the limited internal space of the liquid-filled vibration isolator, it is possible to secure a space (space) for the diaphragm to be displaced, and as a result, the diaphragm comes into contact with other members, It is possible to suppress damage and the like.

  Here, in the conventional product, the flow of the liquid flowing from the main liquid chamber into the sub liquid chamber and the liquid flowing out from the sub liquid chamber into the main liquid chamber with respect to the member that presses the diaphragm (a member corresponding to the direct acting female thread portion) When the flow acts as a flow pressure, the direct pressure female screw portion corresponding member falls due to the flow pressure, and the position is displaced, so that the diaphragm can be appropriately pressed to a predetermined position of the partition (that is, the orifice opening). There was a problem of disappearing.

  On the other hand, according to the present invention, the engaging claw of the direct acting female screw portion is engaged with the guide portion (guide groove). Therefore, even when the above-described fluid pressure acts on the direct acting female screw portion. By engaging the engaging claw with the guide groove, it is possible to avoid the position of the linearly-moving female threaded portion falling like the conventional product and causing a positional shift. Therefore, since the diaphragm can be pressed to a predetermined position of the partition and the first orifice can be reliably closed, the desired characteristic (fluid flow effect) can be exhibited stably.

  In addition, a member for guiding the linearly-moving female screw portion (guided in the axial direction of the screw while restricting rotation) can be separately provided such as being attached to the second mounting tool, etc. In this case, since the number of parts of the switching means increases and the structure becomes complicated, there is a problem that the assembly work becomes complicated and the manufacturing cost increases.

  On the other hand, in the present invention, as described above, since the member for guiding is configured to be shared by the case portion of the driving device, the driving device, the rotating male screw portion, and the direct acting female screw portion are provided. The switching means can be configured as an integrated unit. Therefore, in the assembly work of the liquid filled type vibration isolator, the switching means can be assembled in advance and incorporated as one unit, so that the assembly work can be simplified and the manufacturing cost can be reduced. There is.

According to the hydraulic antivibration device according to claim 2, in addition to the effects of the hydraulic antivibration device according to claim 1 Symbol placement, as well as a convex set of convex portions on the pressing surface of the linear motion female thread portion Since the concave portion for receiving the convex portion is formed in the pressed surface of the diaphragm that is pressed against the pressing surface of the linear motion screw portion, the flow of liquid flowing from the main liquid chamber to the sub liquid chamber Even when the flow of the liquid flowing out from the sub liquid chamber to the main liquid chamber acts on the diaphragm as a flow pressure, the protruding portion of the linear motion screw portion is received in the recessed portion of the diaphragm, so that the lateral displacement of the diaphragm There is an effect that can be suppressed.

  As a result, the positional relationship between the linearly-moving female thread portion and the diaphragm can be maintained, so that the first orifice can be reliably closed by the diaphragm, and desired characteristics (fluid flow effect) can be stably obtained. . Moreover, it can suppress that parts other than the to-be-pressed surface of a diaphragm are pressed by the linear motion internal thread part, and a diaphragm is damaged.

  Further, according to the present invention, the recessed portion of the diaphragm is configured such that the opening portion is configured to have a larger diameter than the outer diameter of the projecting portion of the linear motion female screw portion, and the bottom portion is configured to have a smaller diameter than the opening portion. Therefore, when the pressing surface of the linear motion female screw portion presses the diaphragm against the partition body, the convex configuration of the linear motion female screw portion is provided. The portion can be guided to the bottom by the inclined surface of the recessed portion.

  As a result, even if the diaphragm floats up from the linear motion female screw portion due to the above-described fluid pressure and is largely laterally displaced, if the convex portion of the linear motion female screw portion is received in the concave portion of the diaphragm, the linear motion female screw By moving the part toward the partition (directly moving), the convex part can be guided to the bottom using the inclined surface of the concave part, and the diaphragm can be centered with respect to the direct-acting female screw part. There is an effect that can be done.

  As a result, the positional relationship between the linearly-moving female thread portion and the diaphragm can be maintained, so that the first orifice can be reliably closed by the diaphragm, and desired characteristics (fluid flow effect) can be stably obtained. . Moreover, it can suppress that parts other than the to-be-pressed surface of a diaphragm are pressed by the linear motion internal thread part, and a diaphragm is damaged.

  DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, preferred embodiments of the invention will be described with reference to the accompanying drawings. FIG. 1 is a cross-sectional view of a liquid-filled vibration isolator 100 according to an embodiment of the present invention.

  This liquid-filled vibration isolator 100 is a vibration isolator for supporting and fixing an automobile engine and reducing vibration transmitted from the engine to the vehicle body frame, and is attached to the engine side as shown in FIG. The first mounting bracket 1 to be mounted, the cylindrical second mounting bracket 2 to be mounted on the side of the vehicle body frame below the engine, and the vibration-proof base 3 that connects these and is made of a rubber-like elastic body are mainly provided. Yes.

  The first mounting bracket 1 is formed of an aluminum alloy or the like in a substantially columnar shape, and as shown in FIG. 1, a fastening hole 1a for fastening a mounting bolt on the engine side is recessed on the upper surface (upper side surface in FIG. 1). It is installed. A positioning projection 1b is provided on the side of the fastening hole 1a. Further, the lower part of the first mounting bracket 1 is formed so as to project in a flange shape in the outer diameter direction, and this projecting part is embedded in the vibration isolation base 3.

  The second mounting bracket 2 includes a cylindrical metal fitting 6 on which the vibration-proof base 3 is vulcanized and a bottom metal fitting 7 attached to the lower side of the cylindrical metal fitting 6. As shown in FIG. 1, the cylindrical metal fitting 6 is made of a steel material in a cylindrical shape having an opening that spreads upward, and the bottom metal fitting 7 is made of a steel material in a cup shape with an inclined bottom portion.

  In addition, the mounting bolt 5 and the positioning convex part 7a are protrudingly provided at the bottom part of the bottom metal fitting 7. In addition, an insertion hole 7 b for inserting a power supply line L of the driving device 60 described later is formed in the side portion of the bottom metal fitting 7. The insertion hole 7b is filled with a sealing agent in a state where the power supply line L is inserted, and the inside of the bottom metal fitting 7 is a sealed space.

  The insertion hole 7b is formed in a side portion where the height dimension from the bottom to the opening (the vertical dimension in FIG. 1) is maximum. Thereby, the workability at the time of drilling the insertion hole 7a and the workability at the time of inserting the power supply line L can be improved. Further, as a space for accommodating the power supply line L, a space between the fixing member 19 and the bottom surface of the bottom metal 7 can be used.

  As shown in FIG. 1, the anti-vibration base 3 is formed from a rubber-like elastic body in a substantially truncated cone shape, and is vulcanized between the lower surface side of the first mounting bracket 1 and the upper end opening of the cylindrical fitting 6. It is glued. Further, a rubber film 3a covering the inner peripheral surface of the cylindrical metal fitting 6 is connected to the lower end portion of the vibration isolating base 3, and orifice forming walls 31 and 32 of an orifice metal fitting 30 to be described later are connected to the rubber film 3a. It is in close contact.

  As shown in FIG. 1, the upper end portion (upper side in FIG. 1) of the vibration isolating base 3 is provided with a covering portion 3 b that covers the protruding portion of the first mounting bracket 1, and this covering portion 3 b is attached to the stabilizer bracket 8. By contacting, it is configured to obtain a stopper action at the time of large displacement. The stabilizer fitting 8 is caulked and fixed to the upper end portion of the cylindrical fitting 6.

  The diaphragm 9 is formed in a rubber film shape having a bellows shape from a rubber-like elastic body. As shown in FIG. 1, the diaphragm 9 is attached to the second attachment fitting 2 (between the tubular fitting 6 and the bottom fitting 7). It is attached. As a result, a liquid sealing chamber 11 is formed between the upper surface side of the diaphragm 9 and the lower surface side of the vibration isolation base 3.

  The liquid enclosure 11 is filled with an antifreeze liquid (not shown) such as ethylene glycol. As shown in FIG. 1, the liquid enclosure chamber 11 is divided into a main liquid chamber 11A on the vibration isolator base 3 side (upper side in FIG. 1) and a sub liquid chamber on the diaphragm 9 side (lower side in FIG. 1) by a partition body 20 described later. It is partitioned into two rooms with 11B.

  The diaphragm 9 is vulcanized and bonded to a doughnut-shaped mounting plate 10 (see FIG. 7). As shown in FIG. 1, the mounting plate 10 is located between the cylindrical metal fitting 6 and the bottom metal fitting 7. By being caulked and fixed, the second mounting bracket 2 is attached.

  As shown in FIG. 1, the partition body 20 includes an orifice fitting 30 configured in a substantially cylindrical shape having an opening on the bottom side (lower side in FIG. 1), and a disk fitted from the bottom side opening of the orifice fitting 30. The bottom plate metal fitting 40 is formed. The orifice fitting 30 and the bottom plate fitting 40 are made of an aluminum alloy.

  Here, as shown in FIG. 1, the anti-vibration base 3 includes a partition receiving step 3c formed as a step over the entire circumference on the lower surface side (lower side in FIG. 1), and this partition receiving step 3c. Locks the upper end surface of the partition 20 (orifice fitting 30). In the assembled state of the liquid-filled vibration isolator 100, the partition receiving step 3c is compressed and deformed, and the elastic restoring force of the partition receiving step 3c acts on the partition 20 as a holding force. Thereby, the partition 20 can be clamped and fixed firmly and stably.

  As shown in FIG. 1, the lower surface side of the partition member 20 (orifice fitting 30) is in contact with the upper surface of the clamping member 18, and the outer edge of the clamping member 18 is the second mounting bracket 2 (cylinder). Therefore, the partition body 20 can be firmly held between the clamping member 18 and the partition body receiving step portion 3c of the vibration isolating base 3. As a result, even when a large amplitude or high frequency amplitude is input, chattering of each member can be suppressed, thereby avoiding the influence on the dynamic characteristics due to positional deviation or resonance of each member. Can do.

  As shown in FIG. 1, the partition body 20 is formed with two flow paths of a first orifice 21 and a second orifice 22. The first orifice 21 and the second orifice 22 are orifice passages for communicating the main liquid chamber 11A and the sub liquid chamber 11B, and switching control by the switching device 50 is performed on the first orifice 21.

  That is, the liquid-filled vibration isolator 100 uses the two flow paths of the first orifice 21 and the second orifice 22 while the first orifice 21 is in communication (see FIGS. 16 and 17) during idling. Thus, while obtaining a low dynamic spring characteristic in the idle region (f = f-I, see FIG. 20) (see FIG. 20), the first orifice 21 is shut off during the shake (see FIGS. 18 and 19). By using only the second orifice 22 as a flow path, the liquid column resonance frequency is changed to obtain a high attenuation characteristic in the shake region (f = f−S, see FIG. 20) (see FIG. 20).

  As described above, the switching device 50 presses the diaphragm 9 against the partition body 20 or separates it from the partition body 20, thereby connecting the first orifice 21 (between the main liquid chamber 11 </ b> A and the sub liquid chamber 11 </ b> B). As shown in FIG. 1, a drive device 60 having a rotation shaft 61 and rotationally driving the rotation shaft 61 and a screw fixed to the rotation shaft 61 of the drive device 60 are screwed on the outer peripheral surface as shown in FIG. Rotating male screw portion 70 in which 72 is formed, linear moving female screw portion 80 in which a female screw 80b that can be screwed into the male screw 72 of the rotating male screw portion 70 is formed on the inner peripheral surface, and the linear moving female screw A guide groove 63 is provided as a guide portion for guiding the portion 80 in the axial direction of the screw (vertical direction in FIG. 1).

  As shown in FIG. 1, the driving device 60 of the switching device 50 is fastened and fixed to the bottom portion 19 a (see FIG. 8) of the fixing member 19 configured in a bottomed cylindrical shape. The fixing member 19 has an overhanging flat plate portion 19c (see FIG. 8) caulked between the cylindrical metal fitting 6 and the bottom metal fitting 7, and is fixed to the second mounting metal fitting 2. The rotating male screw portion 70 can be rotated at a fixed position (fixed position) with respect to the partition body 20.

  According to the switching device 50, when the drive device 60 rotates the rotary shaft 61 to rotate the rotary male screw portion 70 at the fixed position, the male screw 72 and the direct acting female screw portion 80 of the rotary male screw portion 70 are rotated. By rotation with the female screw 80b, the direct acting female screw portion 80 is rotated, and the rotation of the direct acting female screw portion 80 to which this rotation is given is regulated by the guide portion (guide groove 63). It is guided in the axial direction of the screw (vertical direction in FIG. 1), and is moved forward or backward with respect to the partition body 20.

  As a result, the rotation male screw portion 70 is rotated in the reverse rotation direction, and the linear motion female screw portion 80 is moved (advanced) in a direction close to the partition body 20 (upward in FIG. 1). The diaphragm 9 is pressed against the partition body 20 by this to close the first orifice 21, and the rotating male screw portion 70 is rotated in the forward rotation direction, so that the linearly moving female screw portion 80 is separated from the partition body 20 (see FIG. 1 (downward), the diaphragm 9 can be detached from the partition 20 and the first orifice 21 can be opened (see FIGS. 16 to 19). The detailed configuration of the switching device 50 will be described later with reference to FIGS. 9 to 13.

  As described above, according to the present embodiment, since the guide portion 63 restricts the rotation of the linear motion female screw portion 80 and allows only the linear motion (straight movement), the linear motion female screw portion 80 is configured. It is possible to avoid twisting of the diaphragm 9 that is pressed against.

  Next, referring to FIGS. 2 to 4, the orifice fitting 30 constituting the partition 20 will be described. 2A is a top view of the orifice fitting 30, and FIG. 2B is a bottom view of the orifice fitting 30. FIG.

  3A is a cross-sectional view of the orifice fitting 30 taken along line IIIa-IIIa in FIG. 2A, and FIG. 3B is a cross-sectional view of the orifice fitting 30 taken along line IIIb-IIIb in FIG. FIG. 3C is a cross-sectional view of the orifice fitting 30 taken along the line IIIc-IIIc in FIG. FIG. 4 is a perspective view of the orifice fitting 30.

  The orifice fitting 30 is a member constituting the partition 20 together with a bottom plate fitting 40 described later, and is formed in a substantially cylindrical shape having an axis O from a metal material such as an aluminum alloy, as shown in FIGS. Yes.

  On the upper and lower ends of the orifice fitting 30 in the axial direction (vertical direction in FIG. 3), substantially flange-shaped orifice forming walls 31 and 32 are formed to project outward in the radial direction. As shown in FIG. 3B, the second orifice 22 is formed between the opposed surfaces of the orifice forming walls 31 and 32.

  As described above, the orifice forming walls 31 and 32 are in close contact with the rubber film 3a covering the inner periphery of the cylindrical metal fitting 6 to form the second orifice 22 having a substantially rectangular cross section (see FIG. 1). . Further, as shown in FIGS. 2 to 4, a vertical wall 33 that connects the orifice forming walls 31 and 32 is formed on the outer peripheral surface of the orifice fitting 30, and the second orifice 22 is divided by the vertical wall 33. Has been.

  Further, as shown in FIGS. 2 to 4, the upper and lower orifice forming walls 31 and 32 are provided with notches 31a and 32a formed by notching a part in the circumferential direction. These notches 31a and 32a are openings serving as entrances and exits of the second orifice 22 in the main liquid chamber 11A and the sub liquid chamber 11B. That is, one end of the second orifice 22 communicates with the first liquid chamber 11A through the notch 31a, and the other end of the second orifice 22 communicates with the second liquid chamber 11B through the notch 32a (see FIG. 1).

  As shown in FIGS. 2 to 4, the orifice fitting 30 is provided with a lid portion 34 on the inner peripheral side, and the upper surface side (upper side in FIG. 3) opening is closed by the lid portion 34. The lid portion 34 includes an opening 34a that is formed in the thickness direction (the vertical direction in FIG. 3A).

  The opening 34a is an opening serving as an entrance / exit of the first orifice 21 (see FIG. 1) on the main liquid chamber 11A side, and when a bottom plate metal fitting 40, which will be described later, is fitted from the bottom surface side opening of the orifice metal fitting 30, It is arranged at a position that coincides with the start end of the concave groove 41 that is recessed in the upper surface of the bottom plate metal fitting 40 (the end in the clockwise direction in the top view of the bottom plate metal fitting 40, see FIG. 5A) (see FIG. 1). .

  Next, with reference to FIG. 5, the bottom plate metal fitting 40 constituting the partition body 20 will be described. Fig.5 (a) is a top view of the baseplate metal fitting 40, FIG.5 (b) is sectional drawing of the baseplate metal fitting 40 in the Vb-Vb line | wire of Fig.5 (a).

  As described above, the bottom plate metal fitting 40 is a member that is fitted from the bottom side opening of the orifice metal fitting 30 and constitutes the partition body 20 together with the orifice metal fitting 30. As shown in FIGS. 5 (a) and 5 (b), the bottom plate metal fitting 40 is formed in a disk shape having an axis O from an aluminum alloy, and has a groove 41 formed in a top surface and a shaft O. And a through hole 42 drilled along.

  The concave groove 41 is a concave groove for forming the first orifice 21 between the above-described lid portion 34 of the orifice fitting 30 (see FIG. 1), and as shown in FIG. 5 (a front side surface in FIG. 5A) is curved and extended in an arc shape with the axis O as the center, and the terminal end (starting end in the clockwise direction in the top view of the bottom plate metal fitting 40) penetrates. It communicates with the hole 42. In addition, as shown in FIG.5 (b), the concave groove 41 is comprised by the groove shape of a substantially rectangular cross section.

  When the bottom plate metal fitting 40 is fitted from the bottom opening of the orifice metal fitting 30 and the bottom surface of the orifice metal fitting 30 (lid portion 34) is covered with the upper surface of the bottom plate metal fitting 40 (see FIG. 1), a part of the first orifice 21 is covered. A curved flow path (concave groove 41) is formed between the lid portion 34 and the bottom plate fitting 40. As described above, in this case, the opening 34a of the lid portion 34 is positioned on the start end side of the flow path (concave groove 41), and the first orifice 21 is communicated with the main liquid chamber 11A side.

  The flow path that forms the first orifice 21 together with the through-hole 42 and the above-described concave groove 42, and as shown in FIGS. 5A and 5B, the end of the concave groove 41 (viewed from the top surface of the bottom plate metal fitting 40). At the start end in the clockwise direction), and is formed as a through hole that penetrates the bottom plate metal 40 linearly along the axis O (that is, a through hole having a constant cross-sectional area along the axis O). ing. The cross-sectional shape of the through hole 42 is formed in a circular shape with the axis O as the center, as shown in FIG.

  As described above, when the bottom surface of the orifice fitting 30 (lid portion 34) is covered with the top surface of the bottom plate fitting 40 (see FIG. 1), the opening above the through hole 42 (upper side in FIG. 5B) is opened by the lid portion 34. A linear flow path (through hole 42) that is closed and forms a part of the first orifice 21 is formed. As a result, one end of the first orifice 21 communicates with the first liquid chamber 11A through the opening 34a, and the other end of the first orifice 21 passes through the opening below the through hole 42 (the lower side in FIG. 5B). It communicates with the two-liquid chamber 11B (see FIG. 1).

  Next, the clamping member 18 will be described with reference to FIG. 6A is a top view of the clamping member 18, and FIG. 6B is a cross-sectional view of the clamping member 18 taken along the line VIb-VIb in FIG. 6A.

  The clamping member 18 is a member for clamping the partition body 20 between the partition body receiving step portion 3c (see FIG. 1). As shown in FIGS. 6 (a) and 6 (b), a steel material is used. To a multi-stage cylindrical shape having an axis O.

  That is, as shown in FIGS. 6 (a) and 6 (b), the clamping member 18 has an annular outer peripheral flat plate portion 18a that is annular when viewed from above, and a cylindrical shape that is erected from the inner peripheral side of the outer peripheral flat plate portion 18a. A first cylindrical portion 18b, an annular inner peripheral flat plate portion 18c connected to the upper end of the first cylindrical portion 18b, and a cylindrical shape standing from the inner peripheral side of the inner peripheral flat plate portion 18c. A second cylindrical portion 18d.

  The outer peripheral flat plate portion 18a is a portion that is caulked and fixed to the second mounting bracket 2 (between the cylindrical bracket 6 and the bottom bracket 7), and the first cylindrical portion 18b is in close contact with the lower end portion of the rubber film 3a. This is the part to be sealed. The inner peripheral flat plate portion 18c is a portion for pressing and holding the lower end surface of the partition body 20 (orifice fitting 30), and the upper surface side (the upper side in FIG. 6B) is below the orifice fitting 30. It is configured as a flat surface corresponding to (adhering to) the end surface.

  As shown in FIG. 6B, the inner peripheral flat plate portion 18c includes an opening 18c1 formed in the thickness direction (the vertical direction in FIG. 6B). The opening 18c1 is an opening serving as an entrance / exit of the second orifice 22 (see FIG. 1) on the side of the sub-liquid chamber 11B, and as shown in FIG. It is formed into a shape.

  Here, when the liquid-filled vibration isolator 100 is assembled, the opening 18c1 of the clamping member 18 overlaps (coincides with) the notch 32a (see FIGS. 2 to 4) formed in the orifice forming wall 32 of the orifice fitting 30. The relative circumferential position of the clamping member 18 with respect to the orifice fitting 30 is determined so as to be a position).

  The second cylinder portion 18d is a portion for increasing the rigidity of the clamping member 18, and as shown in FIG. 6B, the upper end is bent inward (axial center O side). An opening is opened at the upper end of the second cylinder portion 18d. Thereby, interference with the diaphragm 9 can be avoided. Further, the outer diameter of the second cylindrical portion 18d is slightly smaller than the inner diameter of the orifice fitting 30, and a gap is formed between them (see FIG. 1). Thereby, assembly work can be made efficient.

  Next, the diaphragm 9 will be described with reference to FIG. 7A is a top view of the diaphragm 9, and FIG. 7B is a cross-sectional view of the diaphragm 9 taken along the line VIIb-VIIb in FIG. 7A.

  The diaphragm 9 is a part that forms the liquid sealing chamber 11 between the vibration isolating base 3 and plays a role of opening and closing the first orifice 21 (see FIGS. 1 and 17). As shown in (b), it is formed as a rubber film having a bellows shape from a rubber-like elastic body, and is formed in a shape symmetrical to the axis O.

  The diaphragm 9 is vulcanized and bonded from a steel material to a mounting plate 10 configured in an annular shape when viewed from above. As described above, the mounting plate 10 is interposed between the cylindrical metal fitting 6 and the bottom metal fitting 7. By being caulked and fixed, it is attached to the second mounting bracket 2 (see FIG. 1).

  As shown in FIG. 7B, the diaphragm 9 is formed as a rubber film having a bellows-shaped cross section and is located on the mounting plate 10 side, and is connected to the bellows film part 12 and positioned on the axis O side. The pressing film part 13 to be provided.

  The bellows membrane portion 12 is an elastic membrane that changes the volume of the auxiliary liquid chamber 11B by elastically deforming when the fluid flows between the main liquid chamber 11A and the auxiliary liquid chamber 11B (see FIGS. 16 to 19). ). On the other hand, in addition to the function as the elastic film described above, the pressing film portion 13 plays a role of opening and closing the first orifice 21 (see FIGS. 16 to 19).

  The pressing film portion 13 is a portion that is pressed against the bottom plate metal fitting 40 of the partition body 20 by the linear motion female screw portion 80 of the switching device 50 and is in contact with the periphery of the through hole 42 on the lower surface of the bottom plate metal fitting 40 (see FIG. 1), as shown in FIG. 7A and FIG. 7B, it is configured in a disc shape that is thicker than the bellows membrane portion 12.

  As shown in FIGS. 7A and 7B, the pressing film portion 13 includes a closing surface 13a and a pressed surface 13b. The closing surface 13a is a flat surface in contact with the periphery of the through hole 42 on the lower surface of the bottom plate metal fitting 40 (see FIG. 19), and is configured as a surface perpendicular to the axis O as shown in FIG. In addition, it is configured in a circular shape having a larger diameter (approximately three times) than the through hole 42. Therefore, even when the pressing film portion 13 is eccentric, the bottom plate metal fitting 40 can be contacted without a shortage around the through hole 42.

  As shown in FIGS. 7A and 7B, a protruding portion 13a1 projects from the closing surface 13a at the center. The protrusion 13a1 is a part for preventing the lateral displacement of the blocking surface 13a with respect to the through hole 42, and is formed in a tapered columnar shape with the axis O as the center. The pressing film portion 13 moves up and down in a state where the protruding portion 13a1 is fitted in the through hole 42 of the bottom plate metal fitting 40, thereby opening and closing the first orifice 21 (see FIGS. 16 to 19).

  The pressed surface 13b is a flat surface pressed by the linear motion female screw portion 80 of the switching device 50 (see FIGS. 16 to 19), and is configured as a surface parallel to the closing surface 13a. As shown in FIG. 7 (b), the pressed surface 13b is formed in a circular shape having a slightly smaller diameter than the pressing surface 82a of the linearly moving female screw portion 80, and the bellows membrane portion is formed on the outer peripheral edge of the pressed surface 13b. 12 is connected in a state of hanging downward.

  Thereby, since the upper end part of the linearly-moving internal thread part 80 can be hold | maintained by the bellows film | membrane part 12 (refer FIG. 16 to FIG. 19), even when the fluid flow pressure acts on the diaphragm 9, from the linearly-moving internal thread part 80 The diaphragm 9 can be prevented from falling off, and the through hole 42 (first orifice 21) can be reliably closed by the pressing film portion 13.

  As shown in FIG. 7B, the pressed surface 13b is provided with a recessed portion 13b1 at the center. The concave portion 13b1 is a portion for receiving a convex portion 82b of a linear motion female screw portion 80, which will be described later, and preventing lateral displacement of the pressed surface 13b with respect to the pressing surface 82a. It is formed in a trapezoidal cone shape.

  That is, the recessed portion 13b1 is inclined from the opening portion to the bottom portion because the bottom portion (upper side in FIG. 7B) is formed in a circular shape having a smaller diameter than the opening portion (lower side in FIG. 7B). An inclined surface 14 is provided. In addition, the bottom part of the recessed part 13b1 is made into the circle | round | yen substantially the same diameter as the front end surface of the convex part 82b (refer FIG. 13) protrudingly provided by the linear motion internal thread part 80. As shown in FIG.

  Thus, since the recessed part 13b1 is the structure provided with the inclined surface 14 inclined toward the bottom part from an opening part, the pressing surface 82a (refer FIG. 13) of the linear motion internal thread part 80 partitions the diaphragm 9 into a partition body. In the case of pressing to 20, the projecting portion 82b of the linearly moving female screw portion 80 can be guided to the bottom portion by the inclined surface 14 of the recessed portion 13b1.

  Accordingly, even when the diaphragm 9 is lifted from the linear motion female screw portion 80 due to the fluid flow pressure of the liquid in the sub liquid chamber 11B and is largely laterally displaced, the convex portion 82b of the linear motion female screw portion 80 is the concave portion of the diaphragm 9. If it is received by 82b, the linearly-moving female screw portion 80 is moved (linearly moved) toward the partition body 20, so that the convex portion 82b is guided to the bottom using the inclined surface 14 of the concave portion 13b1. Thus, the diaphragm 9 can be centered with respect to the linearly-moving female thread portion 80.

  As a result, the positional relationship between the linearly-moving female thread portion 80 and the diaphragm 9 can be maintained, so that the first orifice 21 is reliably closed by the diaphragm 9 and the desired characteristics (fluid flow effect) are stabilized. Obtainable. Further, it is possible to prevent the diaphragm 9 from being damaged by being pressed by the linearly moving female threaded portion 80 other than the pressed surface 13b of the diaphragm 9.

  Here, as described above, the columnar protrusion 13 a 1 centering on the axis O is provided on the closing surface 13 a of the pressing film portion 13. That is, the protruding portion 13a1 is formed at a position corresponding to the recessed portion 13b1. Thereby, even when the recessed portion 13b1 is recessed in the pressed surface 13b, the recessed portion 13b1 avoids a part of the pressing film portion 13 from being locally thinned, and the pressing film portion 13 Durability can be improved.

  Next, the fixing member 19 will be described with reference to FIG. 8A is a top view of the fixing member 19, and FIG. 8B is a cross-sectional view of the fixing member 19 taken along line VIIIb-VIIIb of FIG. 8A.

  The fixing member 19 is a member for fixing the switching device 50 in a fixed position (see FIG. 1). As shown in FIGS. 8A and 8B, the fixing member 19 has an axis O made of a steel material. It has a cylindrical shape at the bottom.

  That is, as shown in FIGS. 7A and 7B, the fixing member 19 includes a bottom portion 19a that is circular when viewed from above, and a cylindrical tube portion 19b that is erected from the outer periphery of the bottom portion 19a. And an overhanging flat plate portion 19c projecting outward in the radial direction and connected to the upper end of the cylindrical portion 19b.

  The bottom portion 19a has a plurality of (three in the present embodiment) mounting holes 19a1 that are arranged at regular intervals in the circumferential direction around the axis O, and one mounting hole 19a1 among the plurality of mounting holes 19a1. And an insertion hole 19a2 disposed to face each other across the axis O.

  The drive device 60 of the switching device 50 is fastened and fixed to the bottom portion 19a by a fastening bolt inserted through the attachment hole 19a1, and the power supply line L of the drive device 60 is expanded to the outside through the insertion hole 19a2 ( (See FIG. 1).

  The overhanging flat plate portion 19c is a portion that is caulked and fixed between the cylindrical metal fitting 6 and the bottom metal fitting 7 (see FIG. 1). As described above, the driving device 60 of the switching device 50 is fixed to the second mounting bracket 2 via the overhanging flat plate portion 19c, so that the rotating male screw portion 70 is fixed to the partition body 20 ( It can be rotated at a fixed position (see FIG. 1).

  In this way, the fixing member 19 is configured in a bottomed cylindrical shape, and the switching device 50 (drive device 60) is fastened and fixed to the bottom portion 19a, while the power supply line L is expanded to the outside from the insertion hole 19a2 in the bottom portion. As will be described later, since the overhanging flat plate portion 19c of the fixing member 19 is fixed to the second fixture 2, these can be handled as one unit (switching unit). Therefore, it is possible to improve the working efficiency when assembling the liquid-filled vibration isolator 100 (the caulking process described later). Moreover, the structure which fixes the switching apparatus 50 to the fixed position with respect to the partition body 20 can be simplified, and reduction of product cost can be aimed at.

  Next, the switching device 50 will be described with reference to FIGS. 9 to 13. FIG. 9 is a partial cross-sectional perspective view of the switching device 50.

  As described above, the switching device 50 presses the diaphragm 9 against the partition body 20 or separates it from the partition body 20, thereby connecting the first orifice 21 (between the main liquid chamber 11 </ b> A and the sub liquid chamber 11 </ b> B). 9 (see FIG. 16 to FIG. 19), as shown in FIG. 9, a driving device 60 having a rotating shaft 61 and rotationally driving the rotating shaft 61, and a rotating shaft 61 of the driving device 60 Rotation male screw portion 70 that is fixed to the outer peripheral surface and has a screw 72 formed on the outer peripheral surface, and a linearly-moving female screw portion that has a female screw 80b that can be screwed to the male screw 72 of the rotary male screw portion 70 on the inner peripheral surface. 80 and a guide portion (guide groove 63) for guiding the linearly-moving female screw portion 80 in the axial direction of the screw (vertical direction in FIG. 9).

  FIG. 10A is a top view of the driving device 60, and FIG. 10B is a side view of the driving device 60. The driving device 60 mainly includes an electric motor 60a (see FIG. 14), a rotating shaft 61 of the electric motor 60a, and a case portion 62 that accommodates these members and forms the outer shape of the driving device 60. The detailed configuration of the electric motor 60a will be described later (see FIG. 14).

  The rotating shaft 61 is a member configured as a rotating shaft of the electric motor 60a (see FIG. 14), and as illustrated in FIGS. 10 (a) and 10 (b), the rotating shaft 61 is configured in a columnar shape from a steel material. It protrudes from an opening opened on the upper surface of the part 62. The rotation center of the rotating shaft 61 is configured concentrically with the screw axes of the rotating male screw portion 70 and the linear motion female screw portion 80 described later.

  As shown in FIG. 10A and FIG. 10B, the case portion 62 is formed in a hollow cylindrical shape from a resin material, and houses the electric motor 60a (see FIG. 14) inside the cylindrical body. At the same time, guide grooves 63 are recessed at a plurality of locations on the side surface (outer circumferential surface) (in this embodiment, four locations that are equally spaced in the circumferential direction).

  The case portion 62 seals the cup-shaped member that forms the upper surface (the front side surface in FIG. 10A) and the side surface, and the lower surface opening (the lower side in FIG. 10B) of the cup-shaped member. These are plate-shaped members that are fastened and fixed by screws.

  The guide groove 63 is a guide portion for guiding the linearly-moving female screw portion 80 (see FIG. 9) in the axial direction of the screw (the vertical direction in FIG. 10 (b)), and FIGS. 10 (a) and 10 (b). As shown in FIG. 10, the pair of side walls 63a are arranged to face each other with a predetermined distance therebetween, and are linearly extended in the axial direction of the rotating shaft 61 (the vertical direction in FIG. 10 (b)).

  The facing interval W1 between the pair of side walls 63a is set to a size value that is equal to or slightly larger than the width dimension W2 of the engaging claw 84 (see FIG. 12B) in the linear motion female thread portion 80. In the assembled state, the engaging claw 84 can be engaged with the guide groove 63 (see FIG. 9).

  As a result, when the rotation of the rotation male screw portion 70 causes rotation of the linear motion female screw portion 80, the rotation of the linear motion female screw portion 80 by the engagement of the guide groove 63 and the engagement claw 84. The linearly-moving female screw portion 80 can be guided in the axial direction of the screw (for example, the vertical direction in FIG. 9).

  As shown in FIG. 10A, the guide groove 63 has a shape obtained by cutting out a part of an annular shape along the outer shape of the case portion 63 in the direction of the axis O, that is, the axis O as the center. It is formed in a shape curved in an arc shape. A system coupling claw 83 of a linearly-moving female thread portion 80 to be described later is also formed corresponding to this shape, so that the engaging claw 83 can be accommodated in the guide groove 63 and the limited space can be effectively utilized. it can. As a result, the switching device 50 can be downsized.

  FIG. 11A is a top view of the rotating male screw portion 70, FIG. 11B is a side view of the rotating male screw portion 70, and FIG. 11C is an XIc of FIG. 11A. It is sectional drawing of the rotation external thread part 70 in the -XIc line.

  The rotating male screw portion 70 is a member that is fixed to the rotating shaft 61 of the driving device 60 and transmits the rotation of the rotating shaft 61 to the direct acting female screw portion 80 (see FIG. 9), and FIG. As shown in FIG. 11 (c), it is configured as a cylindrical body having an axis O from a resin material.

  The rotating male screw portion 70 includes a fixing hole 71, a male screw 72, and a fastening hole 73. The fixing hole 71 is a portion into which the rotating shaft 61 of the driving device 60 is fitted, and is formed as a through-hole having a circular cross-section that is drilled along the axis O and has an inner diameter corresponding to the outer diameter of the rotating shaft 61. It is configured.

  As shown in FIGS. 11A to 11C, the male screw 72 is a screw formed on the outer surface (outer peripheral surface) of the rotating male screw portion 70, and the axis of the screw coincides with the axis O. Configured. As described above, the male screw 72 is screwed into the female screw 80b of the direct acting female screw portion 80, and the rotation of the rotating male screw portion 70 is transmitted to the direct acting female screw portion 80 through the screwing. (See FIG. 9).

  The fastening hole 73 is a screw hole to which a hexagon socket set screw 74 for fixing the rotating shaft 61 inserted through the fixing hole 71 is fastened. As shown in FIG. The outer surface side is communicated with the inner surface side of the fixing hole 71 and is configured as a through hole orthogonal to the axis O.

  Therefore, the hexagon socket set screw 74 is fastened to the fastening hole 73, and the outer surface of the rotary shaft 61 is pressed against the tip of the hexagon socket set screw 74, so that the rotary shaft 61 is fixed to the rotary male screw portion 70. Is done.

  FIG. 12A is a top view of the direct acting female screw portion 80, and FIG. 12B is a bottom view of the direct acting female screw portion 80. FIG. 13 is a cross-sectional view of the linearly-moving female threaded portion 80 taken along line XIII-XIII in FIG.

  The straight female thread portion 80 is a member for pressing the diaphragm 9 against the partition body 20 (see FIG. 1), and as shown in FIGS. 12 and 13, a main body portion 81, a lid plate 82, and an overhang The wall 83 and the engaging claw 84 are mainly provided, and these are integrally formed from a resin material.

  As shown in FIGS. 12 and 13, the main body 81 is a cylindrical member having an axis O, and includes a female screw 81a. As shown in FIG. 13, the female screw 81 a is a screw formed on the inner surface (inner peripheral surface) of the main body 81, and is configured such that the screw axis coincides with the axis O.

  Note that the thickness (dimension in the left-right direction in FIG. 13) of the main body 81 is substantially the same as or slightly thicker (for example, increased by 50%) as a protruding wall 83 and an engaging claw 84 described later. As described above, the male screw 72 of the rotating male screw portion 70 is screwed to the female screw 81a, and the rotation of the rotating male screw portion 70 is transmitted to the direct acting female screw portion 80 through the screwing. (See FIG. 9).

  As shown in FIGS. 12 and 13, the lid plate 82 is a disk-shaped member that closes one end side (upper side in FIG. 13) of the main body 81 in the axis O direction, and includes a pressing surface 82 a, a projecting portion 82 b, and the like. Is provided. The pressing surface 82a is a flat surface for pressing the diaphragm 9, and is formed on the upper surface side (the upper side in FIG. 13) of the lid plate 82 as a circular surface perpendicular to the axis O and viewed from above.

  The protruding portion 82b is a portion that fits into the recessed portion 13b1 that is recessed in the pressed surface 13b of the diaphragm 9 (see FIG. 1), and as shown in FIGS. 12A and 13, the pressing surface 82a. And is formed in a cylindrical shape having an axis O.

  As shown in FIG. 13, the protruding portion 82b is formed in a tapered cylindrical shape whose cross-sectional area decreases as the distance from the pressing surface 82a increases, and the tip of the protruding portion 82b (upper side in FIG. 13) is It is comprised in the circle | round | yen with the same diameter as the bottom part of the recessed part 13b1 mentioned above.

  As described above, the depressed surface 13b of the diaphragm 9 is provided with the recessed portion 13b1 for receiving the protruding portion 82b (see FIG. 7), and therefore flows from the main liquid chamber 11A to the sub liquid chamber 11B. Even when the flow of the liquid or the flow of the liquid flowing out from the sub liquid chamber 11B to the main liquid chamber 11A acts on the diaphragm 9 as a flow pressure, the protruding portion 82b of the direct acting female screw portion 80 is provided with the recessed portion 13b1 of the diaphragm 9. Therefore, the lateral displacement of the diaphragm 9 can be suppressed.

  As a result, the positional relationship between the linearly-moving female thread portion 80 and the diaphragm 9 can be maintained, so that the first orifice 21 is reliably closed by the diaphragm 9 and the desired characteristics (fluid flow effect) are stabilized. Obtainable. Further, it is possible to prevent the diaphragm 9 from being damaged by being pressed by the linearly-moving female threaded portion 80 other than the pressed surface 13b of the diaphragm 9 (that is, the bellows membrane portion 12).

  Further, as described above, the recessed portion 13b1 of the diaphragm 9 is configured to include the inclined surface 14 that is inclined from the opening portion toward the bottom portion (see FIG. 7), and therefore, the pressing surface 82a of the linear motion female screw portion 80. When the diaphragm 9 is pressed against the partition body 20, the projecting portion 82b of the linear motion female screw portion 80 can be guided to the bottom by the inclined surface 14 of the recessed portion 13b1.

  Accordingly, even when the diaphragm 9 is lifted from the linear motion female screw portion 80 due to the fluid flow pressure of the liquid in the sub liquid chamber 11B and is largely laterally displaced, the convex portion 82b of the linear motion female screw portion 80 is the concave portion of the diaphragm 9. If it is received by 82b, the linearly-moving female screw portion 80 is moved (linearly moved) toward the partition body 20, so that the convex portion 82b is guided to the bottom using the inclined surface 14 of the concave portion 13b1. Thus, the diaphragm 9 can be centered with respect to the linearly-moving female thread portion 80.

  As a result, the positional relationship between the linearly-moving female thread portion 80 and the diaphragm 9 can be maintained, so that the first orifice 21 is reliably closed by the diaphragm 9 and the desired characteristics (fluid flow effect) are stabilized. Obtainable. Further, it is possible to prevent the diaphragm 9 from being damaged by being pressed by the linearly moving female threaded portion 80 other than the pressed surface 13b of the diaphragm 9.

  Further, according to the present invention, the recessed portion of the diaphragm is configured such that the opening is configured to have a larger diameter than the outer diameter of the projecting portion of the linearly moving female screw portion, and the bottom is configured to have a smaller diameter than the opening. Therefore, when the pressing surface of the linear motion female screw portion presses the diaphragm against the partition body, the linear motion female screw portion is convexly provided. The portion can be guided to the bottom by the inclined surface of the recessed portion.

  As a result, even if the diaphragm floats up from the linear motion female screw portion due to the above-described fluid pressure and is largely laterally displaced, if the convex portion of the linear motion female screw portion is received in the concave portion of the diaphragm, the linear motion female screw By moving the part toward the partition (directly moving), the convex part can be guided to the bottom using the inclined surface of the concave part, and the diaphragm can be centered with respect to the direct-acting female screw part. There is an effect that can be done.

  As a result, the positional relationship between the linearly-moving female thread portion and the diaphragm can be maintained, so that the first orifice can be reliably closed by the diaphragm, and desired characteristics (fluid flow effect) can be stably obtained. . Moreover, it can suppress that parts other than the to-be-pressed surface of a diaphragm are pressed by the linear motion internal thread part, and a diaphragm is damaged.

  The overhanging wall 83 is a plate-like member that protrudes radially outward from the other end side of the main body 81 in the axial center O direction (that is, the side opposite to the cover plate 82, the lower side in FIG. 13). 12 (a) and FIG. 12 (b), it is formed at four locations that are equidistant in the circumferential direction with the axis O as the center. The overhanging direction of the overhanging wall 83 is a direction orthogonal to the axis O (the left-right direction in FIG. 13).

  The engaging claw 84 is a portion that is engaged with the guide portion 63 in order to guide the linearly-moving female screw portion 80 in the axial direction of the screw (vertical direction in FIG. 13), and is shown in FIGS. As described above, the wall hangs down (extends) in parallel with the axis O from the overhanging wall 83 toward the case 62 side (see the lower side in FIG. 13 and FIG. 9).

  As described above, the width dimension W2 of the engaging claw 84 is set to a dimension value that is equal to or slightly smaller than the facing distance W1 of the pair of side walls 63a in the guide portion 63. 9), by engaging the engaging claw 84 with the guide groove 63, the rotation of the linearly-moving internal thread portion 80 is restricted, and the linearly-moving internal thread portion 80 is in the axial direction of the screw (for example, FIG. 9). Up and down direction).

In addition, as shown in FIG.
It is formed in a shape obtained by cutting a part of an annular shape along the outer shape of the linearly-moving female threaded portion 80, that is, a shape curved on an arc around the axis O. As described above, since the guide groove 63 of the case portion 63 is also formed corresponding to this shape, the engaging claw 83 can be accommodated in the guide groove 63 so that the limited space can be effectively utilized. . As a result, the switching device 50 can be downsized.

  Here, it returns and demonstrates to FIG. According to the liquid-filled type vibration isolator 100 in the present embodiment, the switching device 50 has a guide groove 63 that is recessed in the outer peripheral surface of the case portion 62 and extends along the axial direction of the screw. Two members, a member that accommodates the components of the driving device 60 (such as the electric motor 60a) and a member that guides the linearly-moving female screw portion 80 (guides rotation in the axial direction of the screw while restricting rotation). 62 can also be used. Therefore, the number of parts can be reduced, and the parts cost and manufacturing cost can be reduced accordingly, and the liquid-filled vibration isolator 100 as a whole can be downsized.

  In addition, according to the liquid-filled vibration isolator 100 according to the present embodiment, the switching device 50 includes the linearly-moving female screw portion 80 having the cylindrical main body portion 81 and the other end in the axial direction of the screw of the main body portion 81. A plate-like extending wall 83 projecting outward from the side (the lower side in FIG. 9) along the upper surface of the case portion 62, and an engaging claw 84 extending from the projecting wall 83 toward the case portion 62. And the engagement claw 84 is engaged with the guide groove 63.

  Therefore, it is possible to form a sufficient space on the outer peripheral side of the main body 81 (that is, between the opposing side of the partition body 20 and the overhanging wall 83) while allowing the linearly-moving female screw portion 80 to be guided in the axial direction of the screw. it can. In other words, the limited internal space of the liquid-filled vibration isolator 100 can be effectively used to secure a space (space) for the diaphragm 9 to be displaced. As a result, the diaphragm 9 is in contact with other members. And it can suppress that it breaks.

  In addition, a member for guiding the linearly-moving female thread portion 80 (guided in the axial direction of the screw while restricting rotation) is formed on or attached to the second fixture 2 (for example, the inner surface of the bottom fitting 7). However, in this case, since the number of parts increases and the structure becomes complicated, there is a problem that the assembly work becomes complicated and the manufacturing cost increases.

  In contrast, in the present embodiment, as described above, the member for guiding is configured to be shared by the case portion 62 of the driving device 60, so that the driving device 60 and the rotating male screw portion 70 are directly connected to each other. The switching device 50 can be configured as one unit (switching unit) in which the moving screw portion 80 is integrated. Therefore, in the assembly work of the liquid-filled vibration isolator 100, the switching device 50 can be assembled in advance and assembled as a single unit, so that the assembly work can be simplified and the manufacturing cost can be reduced. .

  Here, contrary to the case of the present embodiment, the switching means 50 can be configured to rotate the female screw side at a fixed position and move the male screw side directly. Rotating the bearing with a complicated structure of the bearing and driving structure increases the component cost and manufacturing cost and lowers the reliability.

  On the other hand, according to the switching device 50 in the present embodiment, as shown in FIG. 9, the male screw side (rotating male screw portion 70) is rotated at the fixed position, and the female screw side (direct acting female screw portion 80). ) Is directly moved, the structure for rotating the male screw 72 at the fixed position can be simplified, and the parts cost and manufacturing cost can be reduced and the reliability can be improved accordingly.

  Further, according to the switching device 50 in the present embodiment, the rotational movement of the male screw 72 (rotating male screw portion 70) is caused by the screwed engagement between the male screw 72 and the female screw 81a. In the case of converting to the straight movement of the screw portion 80), since the pressing surface 82a is provided on one end side of the female screw 81a (linear movement female screw portion 80) that moves straight and the diaphragm 9 is pressed, the member moves linearly. And the member that presses the diaphragm 9 can be combined with the linearly-moving female screw portion 80.

  Therefore, it is not necessary to provide a separate mechanism for transmitting the linear motion between the member that linearly moves and the member that presses the diaphragm 9, so that the number of parts can be reduced. The manufacturing cost can be reduced, and the liquid-filled vibration isolator 100 as a whole can be reduced in size.

  Next, the control device 110 will be described with reference to FIG. FIG. 14 is a block diagram showing an electrical configuration of the control device 110. As illustrated in FIG. 14, the control device 110 includes a CPU 111, a ROM 112, and a RAM 1173, which are connected to the input / output port 115 via the bus line 114. In addition, a plurality of devices such as the rotation speed detection device 120 are connected to the input / output port 115.

  The CPU 111 is an arithmetic device that controls each unit connected by the bus line 114. The ROM 112 is a non-rewritable nonvolatile memory storing a control program executed by the CPU 111, fixed value data, and the like, and the RAM 113 is a memory for storing various data in a rewritable manner when the control program is executed. .

  The ROM 112 stores a program of a flowchart (switching control process) illustrated in FIG. The RAM 113 is provided with a closing flag 113a.

  The blockage flag 113a is a flag indicating whether or not the first orifice 21 is blocked. In other words, the closing flag 113a is turned on when the first internal thread portion 80 presses the diaphragm 9 against the partition body 20 and the first orifice 21 is closed (see the closed state, see FIGS. 18 and 19). (S11 in FIG. 15), when the diaphragm 9 (linear motion screw portion 80) is separated from the partition body 20 and the first orifice 21 is opened (open state, see FIGS. 16 and 19). (S6 in FIG. 15).

  The rotational speed detection device 120 is a device for detecting the rotational speed of an engine (not shown) and outputting the detection result to the CPU 111. The rotational speed detection sensor (not shown) and its rotational speed detection It mainly includes a control circuit (not shown) that processes the detection result of the sensor and outputs it to the CPU 111.

  The vehicle speed detection device 130 is a device for detecting the ground speed of the vehicle with respect to the road surface and outputting the detection result to the CPU 111. The vehicle speed detection sensor (not shown) and the detection result of the vehicle speed detection sensor are processed. And a control circuit (not shown) for outputting to the CPU 111.

  As described above, the driving device 60 is a device for applying a rotational driving force to the rotating male screw portion 70, and an electric motor 60a that applies a rotational driving force to the rotating male screw portion 70 (that is, the rotating shaft 61). A rotary encoder 60b that detects the number of rotations of the electric motor 60a, and a drive circuit that processes the detection result of the rotary encoder 60b and outputs it to the CPU 111, and controls the motor 60a based on a command from the CPU 111 (FIG. Not shown).

  Here, the driving device 60 forms a so-called motor with an encoder by connecting the rotary encoder 60b to the rotating shaft 61 of the electric motor 60a, and the absolute value of the rotating shaft 61 is determined based on the detection signal of the rotary encoder 60b. The position (that is, the origin) is detected, and the number of rotations (rotation amount) from the origin can be controlled.

  In other words, the rotational position of the rotary shaft 61 is positioned at two positions: the origin and a position rotated from the origin by a required number of revolutions (three rotations in the present embodiment) (hereinafter referred to as “blocking position”). It is configured to be able to.

  In the present embodiment, when the rotational position of the rotating shaft 61 is located at the origin, the diaphragm 9 (the linear motion female thread portion 80) is separated from the partition body 20, and the first orifice 21 is opened. (See FIGS. 16 and 17), and when the rotational position of the rotary shaft 61 is located at the closed position, the linearly-moving internal thread portion 80 presses the diaphragm 9 against the partition body 20, and the first orifice 21 A closed state (see FIGS. 18 and 19) is formed.

  Therefore, as will be described later (see FIG. 15), when the CPU 111 determines that the first orifice 21 needs to be opened, the CPU 111 positions the rotational position of the rotary shaft 61 at the origin (S4: Yes and S5). When it is determined that the first orifice 21 needs to be closed, the rotational position of the rotary shaft 61 is positioned at the closed position (S9: Yes and S10).

  In this embodiment, the rotation direction when the rotation position of the rotation shaft 61 is positioned from the origin to the closing position is defined as the reverse rotation direction, and the rotation direction opposite to the reverse rotation direction, that is, the rotation shaft 61 The rotation direction when the rotation position is located from the closed position to the origin is defined as the positive rotation direction.

  Therefore, “rotating the rotating male screw portion in the normal rotation direction or the reverse rotation direction” described in claim 1 corresponds to rotating the rotary shaft 61 in the reverse rotation direction in the present embodiment. “Rotating the rotating male screw portion in the reverse rotation direction or the forward rotation direction” described in Item 1 corresponds to rotating the rotating shaft 61 in the forward rotation direction.

  Next, the switching control process will be described with reference to FIG. FIG. 15 is a flowchart showing the switching control process. This process is a process that is repeatedly executed by the CPU 111 (for example, at an interval of 0.2 ms) while the power of the control device 100 is turned on. By controlling the switching device 50, the direct acting female screw portion 80 is processed. By changing the pressing state of the diaphragm 9 by switching the communication state between the main liquid chamber 11A and the sub liquid chamber 11B, the two dynamic characteristics of the idle characteristic and the shake characteristic are achieved.

  In the description of the switching control process (FIG. 15), in order to explain the communication state between the main liquid chamber 11A and the sub liquid chamber 11B and the two dynamic characteristics of the idle characteristic and the shake characteristic, FIG. Reference is made to FIGS. 16 to 20 as appropriate.

  FIG. 16 is a schematic view of the liquid-filled vibration isolator 100 schematically showing the communication state of the liquid chamber 11, and FIG. 17 is a partial enlarged cross-sectional view of the liquid-filled vibration isolator 100. In addition, in FIG. 16, illustration of the diaphragm 9 interposed between the partition body 20 and the linear motion internal thread part 80 is abbreviate | omitted.

  In the state shown in FIGS. 16 and 17, the rotational position of the rotary shaft 61 is located at the origin, and the diaphragm 9 (linear motion female thread portion 80) is located away from the partition body 20. Corresponds to the opened state. Accordingly, the main liquid chamber 11 </ b> A and the sub liquid chamber 11 </ b> B are in communication with each other through the two flow paths A and B of the first orifice 21 and the second orifice 22.

  In FIG. 16, a two-dot chain line indicated by reference symbol A indicates a flow path of a fluid that flows from the main liquid chamber 11 </ b> A to the sub liquid chamber 11 </ b> B (or vice versa) via the second orifice 22. The two-dot chain line shown indicates the flow path of the fluid that flows from the main liquid chamber 11A to the sub liquid chamber 11B (or vice versa) via the first orifice 21.

  FIG. 18 is a schematic diagram of the liquid-filled vibration isolator 100 schematically showing the communication state of the liquid chamber 11, and FIG. 19 is a partial enlarged cross-sectional view of the liquid-filled vibration isolator 100. In FIG. 18, similarly to the case of FIG. 16, the illustration of the diaphragm 9 interposed between the partition body 20 and the linear motion female screw portion 80 is omitted.

  The state shown in FIGS. 18 and 19 is such that the rotational position of the rotary shaft 61 is located at the closed position so that the linearly-moving internal thread portion 80 presses the diaphragm 9 against the partition body 20. Corresponds to the state of being blocked (blocked). Therefore, the main liquid chamber 11 </ b> A and the sub liquid chamber 11 </ b> B are in communication with each other through only one flow path A of the second orifice 22.

  In FIG. 18, a two-dot chain line indicated by reference symbol A indicates a flow path of a fluid that flows from the main liquid chamber 11 </ b> A to the sub liquid chamber 11 </ b> B (or vice versa) through the second orifice 22. A two-dot chain line shown indicates a flow path of a fluid flowing from the main liquid chamber 11A to the sub liquid chamber 11B via the first orifice 21. However, in FIG. 18, since the first orifice 21 is blocked, the main liquid chamber 11A and the sub liquid chamber 11B are communicated only via the second orifice 22 (flow path A).

  Thus, in the state shown in FIGS. 16 and 17, the two flow paths A and B of the first orifice 21 and the second orifice 22 are used, whereas in the state shown in FIGS. 18 and 19, Since the flow path is only one flow path A by the second orifice 22 and the cross-sectional area and the flow path length of the entire flow path are different, the liquid column resonance in these two states (communication state and cut-off state) is different. It can be generated in the frequency domain (see FIG. 20).

  FIG. 20 is a graph showing the dynamic characteristics of the liquid filled type vibration damping device 100. The horizontal axis corresponds to the frequency f of the input vibration, and the vertical axis corresponds to the storage spring constant Kd and the damping coefficient C.

  In FIG. 20, the storage spring constant Kd-I and the damping coefficient CI shown by the alternate long and short dash line and indicated by the symbol “A + B” are the first orifice 21 and the second orifice in the main liquid chamber 11A and the sub liquid chamber 11B. 22 in the state where the two flow paths A and B communicate with each other (that is, the state shown in FIGS. 16 and 17 in which the diaphragm 9 (the linear motion female screw portion 80) is separated from the partition 20). Assuming the state, it corresponds to the storage spring constant Kd and damping coefficient C) when the input amplitude is fixed to ± 0.05 mm and the frequency is changed.

  On the other hand, in FIG. 20, the storage spring constant Kd-S and the damping coefficient C-S shown by the solid line and indicated by the symbol “A” indicate that the main liquid chamber 11 </ b> A and the sub liquid chamber 11 </ b> B flow in one second orifice 22. Dynamic characteristics (state of FIG. 18 and FIG. 19 in which the linearly-moving internal thread portion 80 presses the diaphragm 9 against the partition body 20) communicated only by the path A (assuming a shake state, the input amplitude is This corresponds to the storage spring constant Kd and damping coefficient C) when the frequency is changed while being fixed to ± 0.5 mm.

  Returning to FIG. Regarding the switching control process, the CPU 111 first determines whether the engine speed is greater than or equal to a threshold value (S1). Note that whether or not the engine speed is equal to or greater than the threshold value is based on the detection result input from the rotational speed detection device 120 (see FIG. 14) and the reference rotational speed stored in the ROM 112 (see FIG. 14). to decide.

  Further, the reference rotational speed stored in the ROM 112 is an engine rotational speed obtained by adding a predetermined variation (for example, a variation due to on / off of an air conditioner compressor) to the engine rotational speed during idling. In this embodiment, the reference rotation speed is set to 700 rpm (= idling rotation speed 600 rpm + fluctuation rotation speed 100 rpm). The CPU 111 can determine whether or not the state of the vehicle is idle by the process of S1.

  Here, with reference to FIG. 20, the anti-vibration performance (dynamic characteristics) required for the liquid-filled anti-vibration device 100 will be described. An idle vibration input (generally, a vibration having an input amplitude of about ± 0.05 mm in a frequency region of 20 Hz to 40 Hz, and in this embodiment, a frequency f−I = 30 Hz) has a low dynamic spring characteristic (that is, The storage spring constant Kd is required to be small), while shake vibration input (generally, vibration with an input amplitude of about ± 0.5 mm in a frequency range of 10 Hz to 20 Hz, is shown in this embodiment. Then, a high attenuation characteristic (that is, a large value of the attenuation coefficient C) is required for f−S = 15 Hz.

  In the present embodiment, two orifices, ie, a first orifice 21 and a second orifice 22 are provided, and two flow paths A and B of the first orifice 21 and the second orifice 22 are provided for input of idle vibration. The value of the storage spring constant Kd-I in the idle region (fI = 30 Hz) is reduced (low dynamic spring characteristics are obtained) by utilizing the liquid flow effect (liquid column resonance) in FIG. ) (“A + B” in FIG. 20), the transmission of vibration during idling is lowered.

  On the other hand, for the input of shake vibration, the flow path B of the first orifice 21 is cut off and only the liquid flow effect (liquid column resonance) in the flow path A of the second orifice 22 is used (FIG. 18 and FIG. 19), by increasing the value of the damping coefficient CS in the shake region (f−S = 15 Hz) (high attenuation characteristics) (“A” in FIG. 20), the vibration during the shake is attenuated. .

  Therefore, in the present embodiment, as will be described later, the diaphragm 9 (linearly driven female thread portion 80) is arranged at a position separated from the partition body 20 so that the first orifice 21 is in a communicating state at the time of idling, as will be described later. While obtaining a low dynamic spring characteristic at the time of idling (f = f-I), when the idling is finished (that is, during traveling of the vehicle), the linear motion female thread portion 80 is set so that the first orifice 21 is cut off. Then, the diaphragm 9 is pressed against the partition body 20 to obtain a high attenuation characteristic during shake (f = f−S).

  Returning to FIG. In the process of S1, when it is determined that the engine speed is not equal to or greater than the threshold value (S1: No), it can be determined that the vehicle is not running and is idling, so the idle region (f = f-I) The main liquid chamber 11A and the sub liquid chamber 11B are communicated with each other through the two flow paths A and B of the first orifice 21 and the second orifice 22 in order to obtain a low dynamic spring characteristic (reducing the value of the storage spring constant Kd). .

  That is, in this case (S1: No), first, in order to confirm the open / closed state of the first orifice 21, it is determined whether the closing flag 113a (see FIG. 14) is off (S2). As described above, the closing flag 113a is turned on when the first orifice 21 is closed (closed state, see FIGS. 18 and 19), while the first orifice 21 is opened (open state). , See FIGS. 16 and 19).

  Therefore, in the process of S2, if it is determined that the closing flag 113a is off (S2: Yes), the first orifice 21 is already open (that is, the first orifice 21 and the second orifice). 22 is in an open state), the switching device 50 is driven, and the communication state between the main liquid chamber 11A and the sub liquid chamber 11B (that is, the open / close state of the first orifice 21). There is no need to switch between. Therefore, in this case (S2: Yes), this switching control process is terminated.

  On the other hand, in the process of S2, when it is determined that the closing flag 113a is not off (that is, is on) (S2: No), the first orifice 21 is in a closed state, and the second orifice 22 is closed. Since only one flow path A is opened, the first orifice 21 is opened so that the two flow paths A and B of the first orifice 21 and the second orifice 22 are opened. It is necessary to switch.

  Therefore, in this case (S2: No), the drive device 60 (see FIG. 9) in the switching device 50 is drive-controlled to switch the first orifice 21 to the open state.

  Note that, as described above, the driving device 60 presses the diaphragm 9 against the partition body 20 by the linear motion female screw portion 80 by positioning the rotation position of the rotation shaft 61 at the closed position, so that the first orifice 21 is The closed state (see FIGS. 18 and 19) is formed, and the rotation position of the rotary shaft 61 is positioned at the origin (the position rotated from the closed position by the required number of rotations (3 rotations) in the forward rotation direction). Thus, the diaphragm 9 (linear motion female thread portion 80) is separated from the partition body 20 to form an open state in which the first orifice 21 is open (see FIGS. 16 and 17).

  In this case, since it is determined that the first orifice 21 needs to be opened (S2: No), the CPU 111 starts with the electric motor 60a in order to position the rotary shaft 61 in the closed position at the origin. Driving in the forward rotation direction is started (S3), and the process waits until the rotation position of the rotation shaft 61 is located at the origin (S4: No).

  When it is determined that the rotational position of the rotary shaft 61 is located at the origin (S4: Yes), the driving of the electric motor 60a is stopped (S5). As a result, the diaphragm 9 (linear motion screw portion 80) can be separated from the partition body 20, and an open state (see FIGS. 16 and 17) in which the first orifice 21 is opened can be formed.

  Therefore, the main liquid chamber 11A and the sub liquid chamber 11B are communicated with each other through the two flow paths A and B of the first orifice 21 and the second orifice 22, so that the two flow paths A and B are used. Utilizing the liquid flow effect (liquid column resonance), as shown in FIG. 20, the value of the storage spring constant Kd-I in the idle region (f = f-I) is decreased (low dynamic spring characteristics are set). Can do. As a result, transmission of vibration during idling can be reduced.

  After the process of S5, the closing flag 113a is turned off to indicate that the first orifice 21 is in an open state, and then this switching control process is terminated.

  On the other hand, if it is determined in the process of S1 that the engine speed is equal to or greater than the threshold value (S1: Yes), it can be determined that the vehicle is running rather than idle, so the shake region (f = f -S) in order to obtain a high attenuation characteristic (increase the value of the attenuation coefficient C), the first orifice 21 is closed, and the main liquid chamber 11A and the auxiliary liquid are formed only by one flow path A by the second orifice 22. The chamber 11B is connected.

  That is, in this case (S1: Yes), first, in order to confirm the open / closed state of the first orifice 21, it is determined whether the closing flag 113a is on (S7). As described above, the closing flag 113a is turned on when the first orifice 21 is closed (closed state, see FIGS. 18 and 19), while the first orifice 21 is opened (open state). , See FIGS. 16 and 19).

  Therefore, in the process of S7, when it is determined that the closing flag 113a is on (S7: Yes), the first orifice 21 is already closed (that is, one piece by the second orifice 22). Only the flow path A is in an open state), it is not necessary to drive the switching device 50 to switch the communication state between the main liquid chamber 11A and the sub liquid chamber 11B (that is, the open / close state of the first orifice 21). Therefore, in this case (S7: Yes), this switching control process is terminated.

  On the other hand, in the process of S7, when it is determined that the closing flag 113a is not on (that is, is off) (S7: No), the first orifice 21 is in an open state, and the first orifice 21 Since the two flow paths A and B of the second orifice 22 are in an open state, the first orifice 21 is closed so that only one flow path A by the second orifice 22 is open. It is necessary to switch.

  Therefore, in this case (S7: No), the drive device 60 (see FIG. 9) in the switching device 50 is driven to switch the first orifice 21 to the closed state.

  Note that, as described above, the drive device 60 forms an open state (see FIGS. 16 and 17) in which the first orifice 21 is opened by rotating the rotation position of the rotary shaft 61 at the origin, and the rotation is also performed. By positioning the rotational position of the shaft 61 at the closed position (the position rotated by the necessary number of rotations (3 rotations) in the reverse rotation direction from the origin), the diaphragm 9 is pressed against the partition body 20 by the linearly-moving female screw portion 80. The first orifice 21 is configured to be closed (see FIGS. 18 and 19).

  In this case, since it is determined that the first orifice 21 needs to be closed (S7: No), the CPU 111 first sets the rotary shaft 61 at the origin to the closed position. Driving in the reverse rotation direction is started (S8), and standby is performed until the rotational position of the rotary shaft 61 is located at the closed position (S9: No).

  If it is determined that the rotational position of the rotating shaft 61 is located at the closed position (S9: Yes), the driving of the electric motor 60a is stopped (S10). Thereby, the linearly-moving internal thread part 80 presses the diaphragm 9 against the partition body 20, and the closed state (see FIGS. 16 and 17) in which the first orifice 21 is closed can be formed.

  Therefore, since the main liquid chamber 11A and the sub liquid chamber 11B are communicated with each other only through one flow path A by the second orifice 22, the liquid flow effect (liquid column) by the flow path A (second orifice 21) is communicated. Using the resonance, as shown in FIG. 20, the value of the attenuation coefficient C-S in the shake region (f = f−S) can be increased (high attenuation characteristics). As a result, vibration associated with vehicle travel can be attenuated.

  After the processing of S11, the closing flag 113a is turned on to indicate that the first orifice 21 is in the closing state, and then this switching control processing is ended.

  As described above, according to the liquid-filled vibration isolator 100 according to the present embodiment, the rotational motion of the driving device 60 (rotating male screw portion 70) is converted into the linear motion (straight motion) of the straight female screw portion 80. Then, the pressing film portion 13 of the diaphragm 9 is pressed against the partition body 20 (bottom plate metal fitting 40) by the pressing surface 82a of the linear moving female screw portion 80 (see FIG. 19), and the linear moving female screw portion 80 is retracted. Since the pressing film portion 13 of the diaphragm 9 is detached from the partition body 20 (bottom plate metal fitting 40), an urging member (elastic spring) for pressing the diaphragm 9 to the partition body 20 as in the conventional product is unnecessary. It can be. Therefore, there is no need to separate the diaphragm 9 from the partition body 20 against the urging force of the urging member as in the conventional product, so that the driving force required for the driving device 60 is suppressed, and the driving is accordingly performed. The device 60 can be reduced in size (reduced capacity).

  As described above, according to the liquid-filled vibration isolator 100 according to the present embodiment, the screw engagement between the male screw 72 of the rotary male screw portion 70 and the female screw 81a of the direct acting female screw portion 80 is utilized. Therefore, it is possible not only to convert the rotational motion into a straight motion and move the linear motion screw portion 80 in the axial direction of the screw (advance and retreat), but also to utilize the wedge force of the screw, Since the force can be exerted as a pressing force, the pressing film portion 13 of the diaphragm 9 is moved by the pressing surface 82 of the direct acting female screw portion 80 even if the driving device 60 is small (with a small output). The partition 20 (the bottom plate metal fitting 40) can be pressed firmly.

  As a result, even when a force for pushing back the diaphragm 9 from the partition body 20 is generated by the hydraulic pressure at the time of vibration input, the diaphragm 9 is firmly pressed against the partition body 20 to ensure that the first orifice 21 is closed. Can be maintained.

  That is, according to the liquid-filled vibration isolator 100 according to the present embodiment, it is possible to avoid the diaphragm 9 from being pushed back by the liquid pressure at the time of vibration input and the first orifice 21 being inadvertently opened. Therefore, desired characteristics during shaking (high attenuation characteristics in the shaking region (f = f−S)) can be reliably exhibited (FIG. 20). Further, since the shake region is a region where a large amplitude vibration is input and the hydraulic pressure becomes high, the above configuration that can reliably maintain the closed state of the first orifice 21 is particularly effective.

  Further, since the linearly-moving female screw portion 80 is configured such that the rotation is restricted by the guide portion 63 and only the linear motion (straight-ahead motion) is allowed, as described above, the rotational motion is converted into the straight-motion motion, While ensuring the high pressing force utilizing the wedge effect, the linearly-moving internal thread portion 80 does not rotate, so that the diaphragm 9 pressed by the linearly-moving internal thread portion 80 can be prevented from being twisted.

  As a result, wrinkles are formed in the diaphragm 9, resulting in a decrease in durability thereof, and a gap is formed by the amount of wrinkles when pressed against the partition body 20, thereby reliably closing the first orifice 21. Inability to obtain desired dynamic characteristics can be suppressed.

  In the conventional product, the spring constant of the urging member (elastic spring) is lowered due to aging deterioration due to use, and there is a possibility that the diaphragm cannot be firmly pressed against the partition body. According to the liquid-filled vibration isolator 100 according to the present embodiment, since the screw engagement between the rotary male screw portion 70 and the direct acting female screw portion 80 is used, the diaphragm 9 is pressed against the partition body 20. It is possible to stably exert the pressing force to be performed over a long period of time.

  Next, a method for assembling the liquid-filled vibration isolator 100 configured as described above will be described with reference to FIGS. 1 to 19. The assembly of the liquid-filled vibration isolator 100 is first performed by vulcanizing and molding the vibration-proof base 3 in a vulcanization mold in which the first mounting bracket 1 and the cylindrical bracket 6 are arranged. The vulcanized parts (see FIG. 1) connected by the vibration isolating substrate 3 are molded (vulcanization process).

  Further, as a process separate from the vulcanization process, the orifice fitting 30 (see FIGS. 2 to 4) and the bottom plate fitting 40 (see FIG. 5) are submerged in the liquid, and the air (air) of both the fittings 30 and 40 is removed. Then, the partition body 20 is assembled by press-fitting the bottom plate metal fitting 40 from the lower opening of the orifice fitting 30 (the lower opening in FIG. 3A) (partitioning body assembling step).

  Then, the partition body 20 assembled in the partition body assembly process is inserted into the vulcanized part vulcanized and formed in the vulcanization process from the lower opening of the tube fitting 6 (lower opening in FIG. 1) in the liquid. (Submerged assembly process).

  Further, in the submerged assembly process, the clamping member 18 (see FIG. 6) is disposed in the liquid while the opening 18c1 is aligned with the notch 32a of the orifice fitting 30 (see FIGS. 2 to 4). At the same time, a diaphragm 9 (see FIG. 7) is arranged (see FIG. 1).

  In addition, as a separate process from these processes, the rotating male screw portion 70 is fixed to the rotating shaft 61 of the driving device 60 with a hexagon socket set screw 74, and the rotating male screw portion 70 is rotationally driven to move directly. By screwing into the screw portion 80, the linearly moving female screw portion 80 is attached to assemble the switching device 50 (see FIGS. 9 to 13), and the drive device 60 is attached to the fixing member 19 (see FIG. 8). Fastening and fixing are performed to assemble a switching unit in which the switching device 50 and the fixing member 19 are integrated (switching unit assembly process).

  As described above, according to the liquid-filled vibration isolator 100 in the present embodiment, the case portion 62 also serves as a guide portion that guides the linear motion female screw portion 80 (see FIG. 9). The device 50 can be configured as a unit. Therefore, in the caulking process to be described later, the switching device 50 can be assembled in advance and incorporated as a single unit (a switching unit integrated with the fixing member 19). Reduction can be achieved.

  In the switching unit assembling process, the rotating shaft 61 of the electric motor 60a is reversely rotated to a position where the rotating shaft 61 cannot be rotated (that is, a position where the upper surface of the rotating male screw portion 70 abuts on the cover plate 82 of the direct acting female screw portion 80). After rotating once in the rotation direction, the rotation is performed by a predetermined rotation in the positive rotation direction, and a positioning step is performed in which the rotation position of the rotation shaft 61 is located at the origin.

  Then, the first assembly assembled in the submerged assembly process is taken out of the liquid, the switching unit assembled in the switching unit assembly process is arranged with respect to the first assembly, and the bottom fitting 7 is arranged. After the electric power supply line L is inserted into the insertion hole 7b of No. 7, the end portion of the cylindrical metal fitting 6 is caulked (caulking process).

  As described above, in the switching unit assembling process, the positioning process for positioning the rotating shaft 61 at the origin is performed. Therefore, in the caulking process, the switching unit is moved in a state where the protruding amount of the linear motion female screw portion 80 is small. Since it can arrange | position with respect to 1 assembly, the penetration | invasion of the air (air) to the subliquid chamber 11B can be prevented. In other words, if the linear motion female screw portion 80 is arranged with respect to the first assembly in a state where the projection amount is large, the linear motion female screw portion 80 presses the diaphragm 9 to cause the displacement of the diaphragm 9, and the secondary liquid Intrusion of air into the chamber 11B is caused. On the other hand, with the above-described configuration, it is possible to suppress the displacement of the diaphragm 9 and suppress the intrusion of air.

  After the caulking process, the assembly of the liquid-filled vibration isolator 100 is completed by caulking and fixing the stabilizer fitting 8 to the tubular fitting 6 with respect to the assembled product after caulking (see FIG. 1). The insertion hole 7b of the bottom metal 7 is filled with the sealant after the power supply line L is inserted and before or after the caulking process.

  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.

  The numerical values (for example, the quantity, size, angle, etc. of each component) given in the above embodiment are merely examples, and other numerical values can naturally be adopted.

  Moreover, the material raised in the said embodiment is an example, and it is naturally possible to employ | adopt another material. For example, each of the above-described parts made of a resin material may be made of an aluminum alloy, or each of the above-mentioned parts made of an aluminum alloy may be made of a resin material.

  In the above-described embodiment, the case where the control of the switching mechanism 50 (that is, the switching of the opening / closing state of the first orifice 21) is executed based on the engine speed is described, but the present invention is not necessarily limited to this. Of course, it is possible to execute based on the state. Examples of other states include vehicle speed. That is, if the vehicle speed detected by the vehicle speed detection device 130 (see FIG. 14) is 0 km / h or less than a predetermined reference value, it is determined that the vehicle is idling, the first orifice 21 is opened, and the vehicle speed is predetermined. If the reference value is exceeded, it may be determined that the above-described shake is occurring and the first orifice 21 may be switched to be closed.

  In the above embodiment, the case where the rotary male screw portion 70 is directly connected to the rotary shaft 61 of the electric motor 60a has been described. However, the present invention is not limited to this, and the rotary shaft 61 and the rotary male screw portion of the electric motor 60a are not necessarily limited thereto. It is of course possible to interpose a speed reduction mechanism with 70. By interposing the speed reduction mechanism, it is possible to further increase the pressing force for pressing the diaphragm 9 against the partition body 20. In addition, if it is the structure which connects the rotation external thread part 70 directly to the rotating shaft 61 like this Embodiment, the response speed at the time of opening and closing the 1st orifice 21 can be sped up.

  In the above-described embodiment, the case where the pressed surface 13b of the diaphragm 9 and the pressing surface 82a of the linearly-moving internal thread portion 80 are configured to be separable has been described. The surface 13b and the pressing surface 82a may be bonded with an adhesive. This prevents the diaphragm 9 from falling off the linearly-moving internal thread portion 80, and suppresses the problem that the diaphragm 9 is laterally displaced and the bellows membrane portion 12 is pressed against the partition 20 by the pressing surface 82a. it can. In addition, if it is the structure in this Embodiment which does not adhere between the to-be-pressed surface 13b and the pressing surface 82a, the man-hour and material which are required for adhesion | attachment can be reduced, and a product cost can be reduced by that much. .

  In the above-described embodiment, the case where the space (air chamber) formed between the diaphragm 9 and the bottom fitting 7 is configured as a sealed space is not limited to this, and is open to communicate with the outside. Of course, it can be configured as a mold space.

  In the above embodiment, the case where the control of the electric motor 60a in the driving device 60 is performed based on the rotation speed (the detection result of the rotary encoder 60b) has been described. However, the present invention is not necessarily limited to this, and other control methods are used. Of course it is possible to adopt. Examples of other control methods include those controlled by drive time and those controlled by drive torque.

  For example, in the case of controlling by the driving time, the timing is started after the driving of the electric motor 60a is started in the processing of S3 or S8, and the predetermined time has elapsed while waiting for the predetermined time in the processing of S4 or S9. After that, the linear motion female screw portion 80 has moved to the movable limit position in the vertical direction (that is, the linear motion male screw portion 80 has pressed the diaphragm 9 against the partition body 20 or the linear motion male screw portion 80 has moved from the partition body 20. Assuming that the electric motor 60a is separated by a predetermined interval, the driving of the electric motor 60a may be stopped in the process of S5 or S10. Thereby, the rotary encoder 60b can be omitted and the product cost can be reduced.

  For example, in the case of controlling with drive torque, a torque sensor is provided on the rotating shaft 61, and after the drive of the electric motor 60a is started in the process of S3 or S8, the drive torque is set to a predetermined torque in the process of S4 or S9. After reaching a predetermined torque while waiting until it reaches, the linearly-moving internal threaded portion 80 moves to the upper and lower movable limit position (that is, the linearly-moving externally threaded portion 80 presses the diaphragm 9 against the partition body 20 or linearly moves). Assuming that the male screw portion 80 is in contact with the rotating male screw portion 70 or the case portion 63, the driving of the electric motor 60a may be stopped in the process of S5 or S10. This prevents the drive of the electric motor 60a from being stopped before the linear motion female screw portion 80 sufficiently presses the diaphragm 9 against the partition body 20 or sufficiently away from the partition body 20, thereby preventing the first movement. The opening or closing of the orifice 21 can be reliably performed without shortage.

  Although the description is omitted in the above embodiment, the convex height of the convex portion 82b in the direct acting female screw portion 80 may be configured to be larger than the concave depth of the concave portion 13b1 in the diaphragm 9. . Specifically, the height of the protruding portion 82b protruding from the pressing surface 82a in the direction of the axis O (vertical direction in FIG. 13) is set, and the recessed portion 13b1 is set to the pressed surface 13b in the direction of the axis O ( The depth is set to be greater than the depth of the recess provided in FIG.

  Thereby, when the pressing surface 82a of the linearly-moving internal thread portion 80 is brought into contact with the pressed surface 13b of the diaphragm 9, and the pressing film portion 13 of the diaphragm 9 is sandwiched between the partition body 20 and pressed. The protruding portion 82b pushes the bottom of the recessed portion 13b1 upward (partition body 20 side) and pushes a part of the pressing film portion 13 into the first orifice 21 (through hole 42). The closing surface 13a of the portion 13 can be brought into close contact with the periphery of the first orifice 21 (through hole 42). As a result, the first orifice 21 can be reliably closed.

It is sectional drawing of the liquid filled type vibration isolator in one embodiment of this invention. (A) is a top view of an orifice fitting, and (b) is a bottom view of the orifice fitting. (A) is sectional drawing of the orifice metal fitting in the IIIa-IIIa line of Fig.2 (a), (b) is sectional drawing of the orifice fitting in the IIIb-IIIb line of Fig.2 (a), (c ) Is a cross-sectional view of the orifice fitting taken along line IIIc-IIIc in FIG. It is a perspective view of an orifice metal fitting. (A) is a top view of a baseplate metal fitting, (b) is sectional drawing of the baseplate metal fitting in the Vb-Vb line | wire of Fig.5 (a). (A) is a top view of a clamping member, (b) is sectional drawing of the clamping member in the VIb-VIb line | wire of Fig.6 (a). (A) is a top view of a diaphragm, (b) is sectional drawing of the diaphragm in the VIIb-VIIb line | wire of Fig.7 (a). (A) is a top view of a fixing member, (b) is sectional drawing of the fixing member in the VIIIb-VIIIb line | wire of Fig.8 (a). It is a fragmentary sectional perspective view of a switching device. (A) is a top view of a drive device, (b) is a side view of a drive device. (A) is a top view of the rotating male screw portion, (b) is a side view of the rotating male screw portion, and (c) is a rotating male screw portion along the line XIc-XIc in FIG. 11 (a). FIG. (A) is a top view of a linear motion internal thread part, (b) is a bottom view of a linear motion internal thread part. It is sectional drawing of the linearly-moving internal thread part in the XIII-XIII line | wire of Fig.12 (a). It is the block diagram which showed the electric constitution of the control apparatus. It is a flowchart which shows a switching control process. It is a schematic diagram of the liquid filled type vibration isolator schematically showing the communication state of the liquid chamber, and corresponds to the state in which the first orifice is opened. It is a partial expanded sectional view of a liquid enclosure type vibration isolator, and corresponds to the state where the 1st orifice was opened. It is a schematic diagram of the liquid filled type vibration isolator which shows the communication state of a liquid chamber typically, and respond | corresponds to the state by which the 1st orifice was obstruct | occluded. It is a partial expanded sectional view of a liquid enclosure type vibration isolator, and respond | corresponds to the state by which the 1st orifice was obstruct | occluded. It is a graph which shows the dynamic characteristic of a liquid enclosure type vibration isolator.

100 Liquid-sealed vibration isolator 1 First mounting bracket (first mounting bracket)
2 Second mounting bracket (second mounting bracket)
6 Cylindrical metal fittings (part of second fixture)
7 Bottom bracket (part of second fixture)
3 Anti-vibration base 11 Liquid enclosure chamber 11A Main liquid chamber 11B Sub liquid chamber 9 Diaphragm 13b Pressed surface 13b1 Concave surface ( concave portion)
14 Inclined surface 20 Partition 21 First orifice 22 Second orifice 30 Orifice fitting (part of partition)
40 Bottom plate bracket (part of partition)
50 switching device (switching means)
60 Driving device 61 Rotating shaft 62 Case portion 63 Guide groove (guide portion)
63a Side wall (part of guide)
70 Rotating Male Threaded Part 72 Male Thread 80 Linear Motion Female Threaded Part 81 Main Body 81a Female Thread 82a Pressing Surface 82b Projecting Part 83 Projecting Wall 84 Engaging Claw

Claims (2)

A first fixture, a cylindrical second fixture, a vibration isolating base that connects the second fixture and the first fixture and is made of a rubber-like elastic body, and the second fixture. A diaphragm which is attached and forms a liquid enclosure chamber with the vibration isolation substrate; a partition body which divides the liquid enclosure chamber into a main liquid chamber on the vibration isolation substrate side and a sub liquid chamber on the diaphragm side; and A first orifice and a second orifice that are formed in the partition and communicate with each other, and the diaphragm is pressed against the partition to close the first orifice, and the diaphragm is separated from the partition. In a liquid filled type vibration damping device comprising: switching means for switching the communication state between the main liquid chamber and the sub liquid chamber by releasing the first orifice from the body,
The switching means has a rotation shaft and rotationally drives the rotation shaft, a rotation male screw portion fixed to the rotation shaft of the drive device and having a screw formed on an outer peripheral surface, and the rotation male screw portion A linearly-moving female screw portion formed on an inner peripheral surface of a female screw that can be screwed into the male screw; and a guide portion that guides the linearly-moving female screw portion in the axial direction of the screw, and the drive device rotates. The shaft is driven to rotate, the rotating male screw portion is rotated at a fixed position, and rotation is applied to the linear motion female screw portion, whereby the linear motion female screw portion to which the rotation is given is guided by the guide portion. , Configured to be movable in the axial direction of the screw,
The linearly-moving female screw portion includes a pressing surface that is formed in a flat surface shape on one end side in the axial direction of the screw and can press the diaphragm,
By rotating the rotary male screw part in the forward rotation direction or the reverse rotation direction and moving the linear motion female screw part in a direction approaching the partition body, the diaphragm is moved by the pressing surface of the linear motion female screw part. Pressing against the partition body closes the first orifice, rotates the rotating male screw portion in the reverse rotation direction or the forward rotation direction, and moves the linearly moving female screw portion in a direction away from the partition body. By causing the diaphragm to detach from the partition body, the first orifice is opened ,
The drive device includes a case portion that forms an outer shape,
The guide portion is configured as a guide groove that is recessed in the outer peripheral surface of the case portion and extends along the axial direction of the screw,
The linearly-moving female screw portion includes a cylindrical main body portion in which the female screw is formed on an inner peripheral surface and the pressing surface is formed on one end side in the axial direction of the screw, and the screw axis of the main body portion. A plate-like projecting wall projecting outward from the other end in the direction along the upper surface of the case part, and an engagement extending from the projecting wall toward the case part and engaged with the guide groove hydraulic antivibration device according to claim Rukoto a nail. The linear motion female screw portion includes a convex portion projecting from the pressing surface, and the diaphragm is concavely provided on a pressed surface pressed by the pressing surface of the linear motion female screw portion. A recessed portion for receiving the portion,
The recessed portion of the diaphragm is configured such that the opening portion is configured to have a larger diameter than the outer diameter of the protruding portion of the linear motion female screw portion, and the bottom portion is configured to have a smaller diameter than the opening portion. With an inclined surface that inclines from the bottom to the bottom,
When the pressing surface of the linear motion female screw portion presses the diaphragm against the partition body, the convex portion of the linear motion female screw portion is guided to the bottom by the inclined surface of the concave portion. claim 1 Symbol placement of hydraulic antivibration device for.

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