WO2010032971A4 - 낮은 고유 진동수를 가지는 진동 절연 시스템 - Google Patents
낮은 고유 진동수를 가지는 진동 절연 시스템 Download PDFInfo
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- WO2010032971A4 WO2010032971A4 PCT/KR2009/005297 KR2009005297W WO2010032971A4 WO 2010032971 A4 WO2010032971 A4 WO 2010032971A4 KR 2009005297 W KR2009005297 W KR 2009005297W WO 2010032971 A4 WO2010032971 A4 WO 2010032971A4
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- elastic member
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- vibration
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/06—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs
- F16F15/067—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs using only wound springs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
- F16F2228/06—Stiffness
- F16F2228/063—Negative stiffness
Definitions
- the present invention relates to a vibration isolation system having a low natural frequency, and more particularly, to a vibration insulation system having a negative stiffness effect in a conventional vibration isolation system, by lowering the rate of change of the potential energy of the entire vibration insulation system according to the displacement of the support body (support: second object), reducing the natural frequency of the vibration insulation system to the lowest value (the natural frequency is 0 Hz in theory) To about 0 Hz to increase the vibration insulation effect.
- vibrations transmitted from the road surface of a bus, a truck, a heavy equipment vehicle, and various transportation equipment to a driver and a passenger through an automobile have adverse effects on the physical aspects such as back pain, headache, stiff shoulders, In addition, the performance of the vehicle is also adversely affected. Therefore, in order to solve such a problem, a vibration isolation system such as a suspension is applied to the various vehicles or devices to absorb shocks or vibrations that may occur when driving on uneven roads Thereby minimizing the vibration.
- a vibration isolation system such as a suspension is applied to the various vehicles or devices to absorb shocks or vibrations that may occur when driving on uneven roads Thereby minimizing the vibration.
- a vibration isolation device is used between the machine and the support for supporting the machine in order to minimize the influence of the vibration generated by the machine.
- a conventional vibration isolation system 300 includes a first object 310, a second object 320, and a main spring 330.
- the damper 310 may include a damper 340 may be additionally included.
- the main springs 330 may be a part of the first object 310 or the second object 320 and may be a part of the first object 310 or the second object 320, Vibration and shock transmitted from one object to the other object are buffered, thereby generating the effect of vibration isolation.
- a method of adjusting the damping value of a damper is widely used in a conventional insulation device, but it is more effective to apply a technique of lowering the natural frequency value of the system.
- the stiffness value of the spring is designed by yielding to each other, so that the natural frequency can not be lowered below a certain limit.
- vibration isolation model of FIG. 1 As the vibration isolating apparatuses to which the vibration isolation model of FIG. 1 is applied, such as the above-mentioned vehicles, vehicles, precision machines, precision measuring apparatuses including buses, trucks, heavy equipment vehicles, motorcycles and various transportation machines, A conventional vibration isolation device for isolating vibration transmitted to a driver of the vehicle will be described in detail.
- FIG. 2 is a perspective view showing a conventional vibration isolation system for a driver's chair equipped with a vertical main spring
- FIG. 3 is a perspective view showing a conventional vibration isolation system for a driver's chair equipped with a horizontal main spring.
- a conventional vibration insulation system includes a lower rail guard 11 fixedly installed on a vehicle body, an upper rail guard 11 located on the upper portion of the lower rail guard 11 and having a seat cushion connected to an upper surface thereof, And an upper rail guard 12 connected to the lower rail guard 11 and the lower rail guard 11 so as to be connected to the lower rail guard 11 and the upper rail guard 12, And a main spring 14 connected to one side of the lower rail guard 11 and the upper rail guard 12 or one side of the support link 13 to buffer vibrations transmitted from the vehicle body .
- the main spring 14 is divided into a vertical main spring using a compression spring and a horizontal main spring using a tension spring depending on the type of the used spring .
- one end of the vertical main spring 14 is fixed to the upper surface of the lower rail guard 11 and the other end is fixed to the upper surface of the upper rail guard 12, And functions to mitigate vibration or shock transmitted to the vibration insulation system.
- both ends of the horizontal main spring 14 are fixed to the left and right link rotating rollers 13a and 13b of the support link 13, respectively, and are transmitted to the vehicle suspension system It functions to mitigate vibration and impact.
- the vibration isolating system for a vehicle used in the related art is constructed so as to buffer vibration generated by mounting the 'X' -shaped support link 13 and the main spring 14 between the upper rail guard 12 and the lower rail guard 11
- the main spring 14 is different in the degree of compression or tension of the main spring 14 depending on the body weight of the driver, that is, the load applied to the seat. Therefore, the structure of the vibration isolation system Have limitations.
- the spring stiffness of the main spring must be lowered. This increases the amount of static deflection of the system and makes the system's original function impossible, so that the stiffness of the main spring can not be lowered below a certain limit.
- the conventional spring-loaded vibration isolation system usually has a natural frequency between 1.5 and 3 Hz, so that the driver has a high transmittance in the low frequency band between 4 and 10 Hz, where the driver feels the most fatigue due to vibration.
- an auxiliary device is added to maintain the potential energy change rate with respect to the displacement of the vibration insulation system as low as possible It is therefore an object of the present invention to provide a vibration isolation system having a very low, i.e., theoretically, a natural frequency of 0 Hz, a vibration isolation system having a natural frequency of substantially less than 1 Hz and close to 0 Hz.
- an apparatus for detecting vibration transmitted between a first object and a second object by mutual motion between the first object and a second object An auxiliary rigidity device for a vibration isolation system installed in a vibration isolation system provided with a spring, wherein the auxiliary rigidity device is installed in a state of being maximally tensioned or maximally compressed during a first installation so that relative motion between the first object and the second object ,
- the initial maximum tensile displacement or the maximum compressive displacement is relieved in accordance with the following equation (1).
- a link unit positioned between the first object and the second object and fixed at one end of the first object and moving together with the upward and downward movement of the first object;
- the first spring has one end connected to the other end of the link, and the second spring has one end connected to the other end of the link, And the other end is connected to the other end of the support.
- the potential energy of the main spring is increased more than the neutral state, and the potential energy of the auxiliary spring is always lower than the neutral state according to the amount of displacement
- the natural frequency of the vibration insulation system is 1 Hz or less by reducing the exchange rate of the potential energy with respect to the kinetic energy of the vibration insulation system.
- the auxiliary spring is installed in a direction perpendicular to a relative motion direction of the first object and the second object.
- the link unit may include a first link fixed to one side of the first object and moving upward and downward together with the movement of the first object, a second link moving up and down the first link to a horizontal displacement of the auxiliary spring, And a third link connected to the second link and allowing the reciprocating displacement of the auxiliary spring to be horizontally reciprocated and guided by a part of the support.
- a vibration isolator comprising: a main spring connected between a first object and a second object to isolate vibration transmitted by a relative motion between the first object and the second object;
- a vibration isolation system comprising a rigid device of the system is provided.
- an upper rail guard fixed to a first object;
- a lower rail guard positioned below the upper rail guard and fixed to the second object;
- a support link coupled between the upper rail guard and the lower rail guard to move the upper rail guard up and down about the lower rail guard;
- a main spring connected between the upper rail guard and the lower rail guard or connected to one side of the support link to buffer vibration transmitted from the first object and the second object;
- a support plate fixedly installed on an upper portion of the second object or the lower rail guard;
- a link housing fixed to one side of the support plate and having a guide portion;
- a third link inserted into the guide portion and slidable in the guide portion so as to be horizontally reciprocated; and
- a second link fixed to one side portion of the upper rail guard and vertically moved together with the movement of the upper rail guard
- a link portion including a first link and a second link connecting the third link and the first link such that the third link is horizontally reciprocated by the upward and downward movement of the first link;
- an auxiliary spring having one end
- the auxiliary spring is installed in a state of being maximally tensioned or maximally compressed when initially installed so that the initial maximum tensile displacement or maximum compressive displacement is relieved by the relative movement of the upper rail guard and the lower rail guard .
- the potential energy of the main spring is increased more than the neutral state, and the potential energy of the auxiliary spring is always lower than the neutral state according to the amount of displacement
- the frequency of the potential energy with respect to the kinetic energy of the vibration insulation system is reduced, so that the natural frequency of the vibration insulation system is preferably 1 Hz or less.
- the auxiliary spring is installed in a direction perpendicular to a relative motion direction of the first object and the second object.
- a vibration isolation system comprising: a first elastic member which absorbs vibrations transmitted between first and second objects relative to each other in a first direction and has a potential energy minimized at a neutral position; A second elastic member whose potential energy changes according to a relative motion of the first and second objects; And a link portion connecting the first object and the second elastic member such that the potential energy of the second elastic member is maximized at the neutral position.
- the potential energy of the first elastic member may increase.
- the potential energy of the second elastic member can be reduced.
- the total potential energy of the first and second elastic members may be minimized at the neutral position.
- the total potential energy of the first and second elastic members may increase.
- the first elastic member may include a compression spring.
- the first elastic member may include a tension spring.
- the second elastic member can be compressed to the maximum at the neutral position.
- the compression spring may be displaced in a second direction different from the first direction, and the second direction may be perpendicular to the first direction.
- the compression spring can be displaced while rotating about one end that is rotatably fixed.
- the second elastic member may include a tension spring which is pulled to the maximum at the neutral position.
- the tension spring may be displaced in a second direction different from the first direction, and the second direction may be perpendicular to the first direction.
- the tension spring can be displaced while rotating about one end that is rotatably fixed.
- the link unit includes: a first link fixed to the first object and moving in the first direction; A second link connected to the first link for switching the moving direction of the first link to the second direction; And a third link having one end connected to the second link and the other end connected to one end of the second elastic member, and the other end of the second elastic member can be fixed.
- the second elastic member includes a tension spring that is displaced in the second direction, and the tension spring can be pulled to the maximum at the neutral position.
- the second elastic member includes a compression spring that is displaced in the second direction, and the compression spring can be compressed to the maximum at the neutral position.
- the link portion includes a first link fixed to the first object and moving in the first direction
- the second elastic member includes a compression spring, one end of the compression spring is connected to the first link, And the other end of the compression spring can be rotatably fixed.
- the compression spring is compressed to the maximum at the neutral position and the compression spring is displaced while rotating about the other end of the fixed compression spring while keeping the compression state according to the relative motion of the first and second objects have.
- the link portion includes a first link fixed to the first object and moving in the first direction and having a curved portion, one end of the second elastic member contacts the curved portion of the first link, The other end of the elastic member can be fixed.
- the second elastic member can be in contact with the curved portion through the roller.
- the second elastic member includes a compression spring, and the compression spring can be in contact with the curved portion while maintaining the compression state according to the relative motion of the first and second objects.
- the curved portion may be formed such that the compression spring is compressed to the maximum at the neutral position.
- the second elastic member may include a tension spring, and the tension spring may be in contact with the curved portion while maintaining a tension state according to the relative motion of the first and second objects.
- the curved portion may be formed such that the tension spring is pulled to the maximum at the neutral position.
- the link portion includes: a first link rotatably connected to the first object; And a second link connected to the first link and having one end rotatably fixed so as to rotate according to the relative motion of the first and second objects, and one end of the second elastic member is connected to the second link And the other end of the second elastic member may be rotatably fixed.
- the second elastic member includes a tension spring, and the one end of the second link may be disposed at a position where the tension spring is pulled to the maximum at the neutral position.
- the second elastic member includes a compression spring, and the one end of the second link may be disposed at a position where the compression spring is compressed most at the neutral position.
- the vibration isolation system to which the auxiliary rigidity device according to the present invention is applied has the following effects as compared with the existing system having only the main springs.
- the natural frequency of the vibration isolation system is theoretically reduced to 0 Hz, substantially the natural frequency is lowered to 1 Hz or less, and is reduced to 0 Hz, so that the shock or vibration transmitted by the relative motion between the first object and the second object is effectively insulated Thereby providing a riding comfort to the passenger or maintaining the precision of the mechanical system.
- the structure is simple and low cost, and it can be easily attached to a conventional vibration insulation system or can be mounted with a simple design change.
- FIG. 1 is a schematic view showing the operation principle of a conventional vibration insulation system
- FIG. 2 to 3 are perspective views showing a vibration insulating system for a vehicle to which the operating principle of the vibration isolation system of FIG. 1 is applied,
- FIG. 4 is a schematic view showing the operation principle of a vibration isolation system having a low natural frequency according to the present invention
- FIG. 5 is a graph showing a change in potential energy of the vibration isolation system having the low natural frequency of FIG. 4,
- FIGS. 6 to 13 are perspective views showing respective forms of the rigid device according to various embodiments of the vibration isolation system having the low natural frequency of FIG. 4;
- FIG. 14 to 18 are perspective views showing the construction and operation principle of a vibration isolation system having a low natural frequency shown in FIG. 4 applied to a suspension for a driver's chair and a main suspension of a vehicle;
- 19 and 20 are a perspective view and a front view showing the construction of the vibration isolation system of FIG. 4 provided on one side of a wheel shaft of a McPerson type suspension,
- FIG. 21 and FIG. 22 are a perspective view and a front view showing the construction of the vibration isolation system of FIG. 4 provided on one side of a wheel shaft of a Wish-bone type suspension,
- 23 and 24 are a perspective view and a front view showing the construction and operation principle of a vibration isolation system for a machinery installation table to which the operation principle of the vibration insulation system according to FIG. 4 is applied,
- FIG. 25 is a schematic view briefly showing the operation principle of a suspension system equipped with the vertical compression type main spring of Figs. 15 and 16. Fig.
- FIG. 26 is a schematic view briefly showing the operation principle of a suspension system equipped with the horizontal tension spring of Figs. 17 and 18.
- FIGS. 27 to 38 are schematic views showing the configuration of the vibration isolation system according to the present invention in accordance with the shape of the main springs, the auxiliary springs and the link portions, and the positions of the link portions.
- FIG. 4 is a schematic view showing the operation principle of a vibration isolation system having a low natural frequency of the present invention
- FIGS. 23 and 24 are perspective views and a front view showing the construction and operation principle of the vibration isolation system for mounting a precision machinery according to FIG. 4;
- FIG. 4
- the curve A shows the change curve of the potential energy of the main spring
- B is a variation curve of the potential energy of the auxiliary spring
- a curve C is a variation curve of the total potential energy of the vibration insulation system of the present invention in which the potential energy of the main spring and the potential energy of the auxiliary spring are added.
- the vibration isolation system 400 includes a first object 410, a second object 420, a main spring (or a second spring) And a damper 440 having a predetermined damping value may additionally be further included.
- the damper 440 may include a main spring 430 and an auxiliary rigidity device 500.
- the low natural frequency means a natural frequency which is theoretically 0 Hz of the vibration insulation system, and is substantially made to be close to 0 Hz by lowering the natural frequency to 1 Hz or less.
- the first object 410 and the second object 420 are parts of the object to which vibration and impact are transmitted.
- the object includes a device and a device for receiving vibration and shock, that is, a vehicle, , Construction equipments, elevators, etc., and vibration isolating devices for mitigating existing vibration and impact may all be equipments and equipments.
- the main spring 430 is positioned between the first object 410 and the second object 420 and is transmitted from one of the first object 410 and the second object 420 to another object Vibration and shock.
- the curve A in FIG. 5 indicates a change in the potential energy of the main spring 430, that is, the relative displacement between the first object 410 and the second object 420
- the curve B shows a potential energy change curve of the auxiliary spring 510, that is, a position energy function of the auxiliary spring 510 in the auxiliary rigidity device 500.
- the curved line C represents the sum of the curves A and B or the sum of the potential energy of the main spring 430 and the potential energy of the auxiliary spring 510 And shows the change curve of the total potential energy.
- the main spring 430 is connected to the first object 410 and the second object 410 of the vibration isolation system 400 of the present invention, such as a curve A (change curve of the potential energy of the main spring)
- the potential energy of the main spring 430 changes with a positive rate of change in accordance with the relative displacement of the main spring 420.
- the main spring 430 is positioned between the weight supported by the first object 410 and the force of the main spring 430, The potential energy has a minimum value in the static deflection state.
- the main spring 430 is displaced from the neutral position to increase the potential energy.
- the auxiliary rigidity device 500 includes a supplementary spring 510, a link portion 520 and a support portion 530.
- the auxiliary rigidity device 500 is additionally mounted on a passive type vibration isolation system that does not require external power Thereby improving the insulation efficiency of vibration.
- the link part 520 is positioned between the first object 410 and the second object 420 and one end of the link part 520 is fixed to one side of the first object 410, And the other end is mounted to be connected to one end of the auxiliary spring 510.
- One end of the support portion 530 is fixed to one side of the second object 420 and the other end thereof fixes the other end of the auxiliary spring 530.
- the auxiliary spring 510 has the greatest potential energy at the neutral position (see FIG. 5). As the relative positions of the first and second objects 410 and 420 change at the neutral position, the potential energy of the auxiliary spring 510 changes with a negative rate of change.
- the auxiliary spring 510 may include a tension spring or a compression spring. An embodiment using a tension spring corresponds to Figs. 6-10, and an embodiment using a compression spring corresponds to Figs. 11-13. For convenience of explanation, the case where the auxiliary spring 510 is a tension spring will be described first.
- auxiliary spring 510 One end of the auxiliary spring 510 is connected to the link portion 520 and the other end is connected to the other end of the support portion 530 so that the link portion 520 is moved up and down together with the first object 410 So that the tensile displacement is changed.
- the auxiliary spring 510 is installed in a state of being maximally tensioned when the auxiliary spring 510 is initially installed so that the up and down vibration is transmitted to the vibration isolation system 400 of the present invention, Quot; means that the initial tensile displacement is changed by the up-and-down motion of the upper portion 520.
- the auxiliary spring 510 has a magnitude of vibration applied to the vibration isolation system 400 of the present invention, such as curve B, which is a variation curve of the potential energy of the auxiliary spring 510, The potential energy of the auxiliary spring 510 changes.
- the auxiliary spring 510 is at the maximum tension at the neutral position, which is a static load state in which the vibration isolation system 400 of the present invention is free from vertical vibration, the potential energy of the auxiliary spring 510 is maximum .
- the tension displacement of the auxiliary spring 510 is reduced, and the potential energy of the auxiliary spring 510 is reduced.
- the potential energy change of the auxiliary spring 510 is changed only by the auxiliary spring 510 (see FIG. 11-13) only at the point where the auxiliary spring 510 is compressed to the maximum at the neutral position, 510) is a tension spring.
- the auxiliary rigidity device 500 may include a link portion 520 and a support portion 530 located between the first and second objects 410 and 420, And can be mounted on the vibration isolation system 400 of the present invention in various structures depending on the change of the shape.
- the link unit 520 includes a first link 521, a second link 522, a third link 523, a circular link 524, and a roller 525 And it is also possible to perform the function of the link unit 520 by a combined structure of a plurality of links or rollers selected from the links 521, 522, 523, and 524 or the rollers 525.
- the natural frequency of the vibration isolation system 400 can be reduced, and the natural frequency can be reduced to less than 1 Hz and closer to 0 Hz in accordance with the design requirement.
- the first link 521 is fixed to the first object 410 by the first object 410 and moves in the same direction as the first object 410 in the moving direction (i.e., vertical direction).
- One end of the second link 522 is connected to the first link 521.
- One end of the third link 523 is connected to the second link 522.
- the other end of the third link 523 is connected to one end of the auxiliary spring 510 and the other end of the auxiliary spring 510 is fixed.
- the second link 522 serves to switch the moving direction of the first link 521 so that the third link 523 is moved in a direction different from the moving direction of the first link 521 .
- the potential of the auxiliary spring 510 is maximized because the auxiliary spring 510 is pulled to the maximum at the neutral position as shown in FIG.
- the third link 523 moves to the right in FIG. 6, and the tensile displacement of the auxiliary spring 510 is reduced.
- the potential energy of the auxiliary spring 510 is reduced. Therefore, the potential energy of the auxiliary spring 510 changes as shown in FIG.
- the rate of change of the total potential energy of the vibration insulation system 400 can be made gentler than that of the conventional vibration insulation system, .
- FIG. 7 shows another embodiment in which the auxiliary spring 510 is a tension spring. 6 is different from the embodiment of FIG. 6 only in that the third link 523 is provided with a wheel so that the movement of the third link 523 can be smoothly performed, and thus a detailed description thereof will be omitted.
- FIG 8 shows another embodiment in which the auxiliary spring 510 is a tension spring, in which the auxiliary spring 510 is at its maximum tension in the neutral position. Only two links 521 and 522 are used here.
- the first link 521 is rotatably connected to the first object 410 and the second link 522 is connected to the first link 521.
- the connecting portion of the first object 410 of the first link 521 is not shown.
- one end of the second link 522 is rotatably fixed, when the first object 410 moves, the second link 522 rotates about the one end rotatably fixed.
- auxiliary spring 510 is connected to the other end of the second link 522, and the other end of the auxiliary spring 510 is rotatably fixed.
- the auxiliary spring 510 of FIGS. 6 and 7 only changes its length, but the auxiliary spring 510 of FIG. 8 changes its length while rotating. This is because the third link 523 shown in Figs. 6 and 7 is omitted.
- one end of the second link 522 which is rotatably fixed, is disposed at a position where the auxiliary spring 510 is pulled to the maximum at the neutral position. 8, the position of one end of the second link 522 is disposed between the one end and the other end of the auxiliary spring 510.
- the auxiliary spring 510 is in the neutral position as shown in FIG. In the neutral position as shown in FIG. 8, since the auxiliary spring 510 is pulled to the maximum, the potential energy of the auxiliary spring 510 becomes maximum.
- the second link 522 rotates about one end of the second link 522, and the tension displacement of the auxiliary spring 510 is reduced. This means that the potential energy of the auxiliary spring 510 is reduced. Therefore, the potential energy of the auxiliary spring 510 changes as shown in FIG.
- auxiliary spring 510 is a tension spring. 6 and 7, except that only the position of the first link 521 is changed. Since the first link 521 is disposed between the one end and the other end of the auxiliary spring 510, the area occupied by the secondary stiffener 500 is reduced, and the secondary stiffener 500 can be downsized.
- Fig. 10 shows a state in which the auxiliary spring 510 is pulled to its maximum in the neutral position, as another embodiment of the tension spring case.
- the circular link 524 having the curved portion 524a is used is different from the previous embodiment.
- the circular link 524 is fixed to the first object 410 and moves in the same direction as the moving direction of the first object 410 (i.e., up and down direction).
- One end of the auxiliary spring 510 contacts the curved portion 524a of the circular link 524 through the roller 525 and the other end of the auxiliary spring 510 is fixed so that the auxiliary spring 510 is displaced in the horizontal direction.
- the tensile displacement of the auxiliary spring 510 is determined according to the shape of the curved portion 524a.
- the curved portion 524a should be formed such that the auxiliary spring 510 is pulled to the maximum at the neutral position.
- the curved portion 524a may have an arc shape.
- the potential energy of the auxiliary spring 510 is maximized.
- the tension displacement of the auxiliary spring 510 is reduced. This means that the potential energy of the auxiliary spring 510 is reduced. Therefore, the potential energy of the auxiliary spring 510 changes as shown in FIG.
- FIG. 11 shows an embodiment in which the auxiliary spring 510 is a compression spring and shows a state in which the auxiliary spring 510 is compressed to the maximum at the neutral position.
- the configuration of the first, second and third links 521, 522 and 523 shown in FIG. 11 is similar to that of FIG. 6, and the point of the compression spring of the auxiliary spring 510 and the fixing position of the auxiliary spring 510 are changed. 11, the left end of the auxiliary spring 510 is fixed. The right end of the auxiliary spring 510 is connected to the third link 523 and the right end of the auxiliary spring 510 is moved as the third link 523 moves.
- the auxiliary spring 510 is maximally compressed at the neutral position as shown in FIG. 11, so that the potential energy of the auxiliary spring 510 becomes maximum.
- the third link 523 moves to the right in FIG. 6, and the right end of the auxiliary spring 510 also moves to the right. This means that the compression displacement of the auxiliary spring 510 is reduced and the potential energy of the auxiliary spring 510 is reduced. Therefore, the potential energy of the auxiliary spring 510 changes as shown in FIG.
- auxiliary spring 510 is a compression spring, in which the auxiliary spring 510 is compressed to its maximum in the neutral position. Only one link 521 is used here.
- the first link 521 is fixed to the first object 410 by the first object 410 and moves in the same direction as the first object 410 in the moving direction (i.e., vertical direction).
- One end of the auxiliary spring 510 is connected to the first link 521, and the other end of the auxiliary spring 510 is rotatably fixed. Accordingly, when the first object 410 moves, the auxiliary spring 510 is rotated and displaced.
- auxiliary spring 510 is a compression spring, in which the auxiliary spring 510 is compressed to its maximum in the neutral position.
- a circular link 524 having a curved portion 524a is used, which is the same as the embodiment of FIG. 10, so that a detailed description will be omitted.
- the auxiliary spring 510 is compressed to the maximum at the neutral position, and when the position of the first object 410 changes at the neutral position, the compression displacement of the auxiliary spring 510 is reduced. Therefore, the potential energy of the auxiliary spring 510 changes as shown in FIG.
- the vibration isolation system 400 of the present invention is applied to a driver's seat or a passenger seat of a vehicle, so that the vibration transmitted to the driver's seat or occupant's seat by the vibration isolation system 400 is isolated, Will be described.
- a vibration isolation system includes a lower rail guard 110, an upper rail guard 120, a support link 130, a main spring 140, (200).
- the upper rail guard 120 is connected to one side of the first object, and the lower rail guard 110 is connected to one side of the second object.
- the first object and the second object refer to a part of the object to which the vibration and the shock are transmitted, and the object may include a device and a device for receiving vibration and shock, that is, a motorcycle, an aircraft, Elevators, etc., and apparatuses and equipments capable of installing vibration isolation devices for alleviating vibration and impact.
- the lower rail guard 110 is fixed to the vehicle body, and one side of each corner is provided with a link connection portion a 131a to be connected to the lower end of the support link 130.
- the upper rail guard 120 is located on the upper portion of the lower rail guard 110 and is equipped with a seat cushion (not shown) on its upper surface and a fixing plate 121 supporting one end of the main spring 140 , And a link connecting portion b (131b) is formed at one side of each corner so as to be connected to the upper end of the support link (130).
- the support link 130 is positioned between the lower rail guard 110 and the upper rail guard 120 and the lower end thereof is fastened to the link connection portion a 131a of the lower rail guard 110,
- the lower rail guard 110 and the upper rail guard 120 are connected to each other by a link connecting portion b 131b of the guard 120.
- the lower rail guard 110 and the upper rail guard 120 ).
- the support link 130 is formed in an 'X' shape in which two links are crossed.
- the support link 130 is folded about a portion where each link crosses at the center thereof to adjust the height of the support link.
- the present invention is not limited to this, and the number of the supporting links 130 may be determined by taking into consideration the use of the vibration isolation system of the present invention or the load applied to the suspension system. It is preferable to be determined.
- the main spring 140 is installed in a vertical state, and one end portion And the other end is supported by the lower surface of the upper rail guard 120 and mounted.
- the main spring 140 is installed in a horizontal state so that both ends of the main spring 140 are connected to the left and right links 130 of the support link 130, And is fixed to the rotary roller 132.
- the main spring 140 is positioned between the lower rail guard 110 and the upper rail guard 120 to buffer the vibration transmitted from the vehicle body.
- main spring 140 an air spring, a leaf spring, or the like is used as the main spring 140 in consideration of the use of the vibration isolation system of the present invention, .
- the main spring 140 has a minimum potential value in a static state in which the driver's weight and the spring force are in equilibrium when the driver sits down, which is a neutral position without vertical vibration.
- the secondary rigidity device 200 includes a support plate 210, a link housing 220, a link portion 230, and an auxiliary spring 240. As shown in FIG.
- the support plate 210 may be directly fixed to the vehicle body so as to support and fix the rigid device, or may be fixedly mounted on the upper surface of the lower rail guard 110 fixed to the vehicle body.
- a link housing 220 having a guide portion 221 is fixedly installed on an upper surface of the support plate 210 and a link portion 230 is inserted into a guide portion 221 of the link housing 220.
- the link unit 230 includes a first link 231, a second link 232, and a third link 233.
- the third link 233 is inserted into the guide portion 221 and is slidable therein so as to be horizontally reciprocated.
- the first link 231 has one end connected to the fixed plate 220 of the upper rail guard 120, And is vertically movable together with the movement of the upper rail guards 120 by being fixedly installed on one side of the upper rail guards 121.
- the second link 232 connects the first link 231 and the third link 233 to each other so that the third link 233 is horizontally reciprocated by the upward and downward movement of the first link 231 .
- a second link 232 connected to the first link 231 corresponds to the upward and downward movement of the first link 231, and the second link 232 is connected to the third link 233 So that the tensile displacement of the auxiliary spring 240 is changed.
- One end of the auxiliary spring 240 is connected to one side of the link 230 and the other end is connected to one side of the support plate 210 so that the third link 233 of the link 230, So that the tensile displacement is changed.
- auxiliary spring 240 is installed in the state of being maximally tensioned or maximally compressed when the auxiliary spring 240 is installed for the first time so that the upper and lower rail guards 120, Quot; means that the tensile or compressive displacement is made to be relaxed.
- the upper rail guard 120 moves up and down, and the first link 231 fixed to the fixed plate 121 of the upper rail guard 120 And moves up and down to operate the second link 232 connected to the first link 231 to reciprocate the third link 233 horizontally.
- the auxiliary spring 240 is arranged in a manner such that the auxiliary spring 240 can be operated in accordance with the magnitude of the vibration applied to the vibration isolation system of the present invention, such as curve B, The potential energy of the spring 240 changes.
- the auxiliary spring 240 is at the maximum tension in the neutral position, which is a static load state in which the vibration isolation system of the present invention does not have vertical vibration, the potential energy of the auxiliary spring 240 is maximized .
- the tensile displacement of the auxiliary spring 240 is smaller than the tensile displacement at the neutral position. Accordingly, the potential energy of the auxiliary spring 240 deviates from the maximum tension state, and the potential energy thereof is reduced.
- FIG. 25 is a schematic view showing the principle of operation of the vibration isolation system in which the main springs 140 installed vertically in FIGS. 15 and 16 are mounted.
- FIG. 26 is a schematic view showing the main springs 140 Is a schematic view briefly showing the operation principle of the vibration isolation system equipped with the vibration isolation system.
- 26A and 26B are views showing a state in which the upper rail guard 120 is moved upwards due to the upward vibration of the vibration transmitted to the vibration isolation system,
- the main springs 140 and the auxiliary springs 240 are connected to each other in the absence of vibration transmitted to the vibration isolation system
- (C) is a view showing a state where the upper rail guard 120 is moved downward due to the downward vibration of the vibration transmitted to the vibration insulation system, and the main spring 140
- the auxiliary spring 240, and the link unit 230 are operated.
- the main spring 140 and the auxiliary spring 240 are positioned at the neutral position So that the potential energy possessed by the main spring 140 maintains a minimum value, and the potential energy possessed by the auxiliary spring 240 maintains a maximum value.
- the potential energy of the auxiliary spring 240 is the maximum value, the sum of the potential energy of the main spring 140 and the auxiliary spring 240, that is, the sum of the potential energy of the entire vibration insulating system becomes minimum, It is possible to maintain the neutral position.
- the main spring 140 is in a static deflection state and the auxiliary spring 240 maintains the maximum tension displacement so that the second link 232 of the link unit 230 and the third The link 233 is in a horizontal state.
- the total vibration energy system and the maximum potential energy points of the main spring 140 and the auxiliary spring 240 are equal to each other at the neutral position irrespective of the body weight, It is necessary to design.
- the main spring 140 increases the potential energy in proportion to the magnitude of the added vibration, and the auxiliary spring 240 generates a potential energy corresponding to the magnitude of the added vibration .
- the change of the po- tential energy of the main spring 140 increases according to the amount of compression or tensile displacement of the main spring 140, ) Is provided such that the potential energy is changed so that the potential energy changes in accordance with the amount of displacement.
- the vertical main spring 140 holds the potential energy of the minimum value when there is no vertical vibration applied to the vibration insulation system of the present invention.
- the length is compressed or tensioned, Energy always increases.
- the auxiliary spring 240 holds the maximum potential energy when there is no vertical vibration applied to the vibration isolation system of the present invention.
- the length of the auxiliary spring 240 is always compressed. It always decreases.
- the main spring 140 increases the potential energy corresponding to the magnitude of the added vibration
- the auxiliary spring 240 increases the potential energy corresponding to the magnitude of the added vibration. In this case, as shown in FIG. 5, The potential energy at the maximum value at the position is reduced.
- the main spring 140 is rotated in a direction corresponding to the magnitude of the added vibration, so that the potential of the main spring 140 is increased.
- the energy is increased and the auxiliary spring 240 decreases the potential energy at the maximum value at the neutral position corresponding to the magnitude of the added vibration.
- the horizontal main spring 140 stretches or compresses the length when the vertical vibration is applied, and when the vibration is applied to the vibration isolation system of the present invention, The potential energy is always increased.
- the auxiliary spring 240 holds the maximum potential energy when there is no vertical vibration applied to the vibration isolation system of the present invention.
- the length of the auxiliary spring 240 is always compressed. It always decreases.
- the rate of change with respect to the displacement of the potential energy of the vibration isolation system of the present invention is reduced,
- the frequency can be lowered and the natural frequency can be lowered to 1 Hz or less according to the design value.
- the change amount of the potential energy of the auxiliary spring 240 using the linear spring decreases the potential energy change rate of the whole system, and the potential energy for the entire system , which means that the natural frequency of the vibration isolation system can be lowered to 1 Hz or less.
- the present invention can reduce the natural frequency of the vibration isolation system by reducing the potential energy change rate of the entire system by using the rigid linear spring.
- FIG. 27 to 38 illustrate the shape of the main spring (whether a tension spring or a compression spring) of the vibration isolation system of the present invention
- the shape of the auxiliary spring whether a tension spring, a compression spring or a leaf spring
- 1 is a diagram showing a configuration of a vibration isolation system of the present invention.
- the mainspring and the auxiliary springs are compression springs or tension springs, so that the change in the potential energy of the vibration isolation system of the present invention is moderate irrespective of the shape of the link portion and the mounting position
- the natural frequency of the vibration isolation system can be lowered and the natural frequency can be reduced to about 1 Hz or less and close to 0 Hz according to the design requirement.
- Figs. 27-32 show the case where the main spring is installed vertically. 27-30, a compression spring is used as the auxiliary spring, and the compression spring is compressed to the maximum at the neutral position. In Figures 31-32, the tension spring is used as the auxiliary spring, and the tension spring is pulled to the maximum at the neutral position. Since various constructions of the negative rigidity device have been described with reference to FIGS. 6-13, those skilled in the art will readily understand the configuration of FIGS. 27-32, and a detailed description thereof will be omitted.
- the vibration isolation system of the present invention is limited to the vibration isolation system applied to the driver's seat of various vehicles.
- the present invention is not limited to this, and may be applied to a vehicle suspension system Or a machine support system that supports the machine.
- the auxiliary rigidity apparatus 500 to which the operating principle of the vibration isolation system 400 of the present invention is applied, is mounted on one side of the wheel shaft 610 of the vehicle, It is possible to realize a configuration in which vibration or shock transmitted from the motor can be isolated.
- the vibration-inducing system 400 in order to reduce vibrations and noise generated in the machine, it is also possible to apply the support between the supports for supporting the weight of the support. At this time, the machine may be positioned above the first object 710, and the support may be located below the second object 720.
- the change of the potential energy of the main spring 730 increases according to the tensile displacement amount of the main spring 730 due to the up-and-down motion of the first object 710 and the second object 720,
- the potential energy of the auxiliary spring of the rigid device 500 is provided so as to be decreased in accordance with the amount of displacement.
- a vibration isolation system mounted on one side of the wheel axle of the vehicle and a vibration isolation system mounted between the support of the machine and the machine, wherein the amount of change in the potential energy of the auxiliary spring reduces the rate of potential energy change of the overall system,
- the operation principle for lowering the natural frequency of the system is the same as the operation principle of the vibration isolation system of the present invention described above with reference to FIG. 4, and therefore, further explanation will be omitted.
- the present invention uses a rigid device in existing systems to keep the rate of change of potential energy of the system in accordance with the displacement low.
- the auxiliary rigidity device applied to a conventional or designed vibration isolating device using only the main spring is designed so that the spring displacement of the secondary rigidity device is parallel to the relative displacement between the first object (mass) and the second object (Fig. 4).
- the auxiliary rigidity device may include a linear spring and a link for interlocking the displacement of the spring with the relative displacement between the first object and the second object.
- the auxiliary spring is installed in a tensioned or compressed state at the time of initial installation so that the potential energy of the auxiliary spring is reduced when the initial tension or compression displacement is relaxed by the relative motion of the first object and the second object .
- the potential energy of the auxiliary spring increases in accordance with the amount of compression or tensile displacement of the existing system main spring, while the potential energy of the auxiliary spring decreases in accordance with the amount of displacement, The rate of change becomes low, and the natural frequency of the vibration insulation system can be maintained at a very low level.
- the auxiliary rigid device includes a vertical movement link (first link) 521 fixed to one side of the first object and performing upward and downward movement together with the movement of the first object, the vertical movement of the first link is a horizontal displacement of the auxiliary spring
- a spring linkage link (third link) 523 that allows the horizontal reciprocating displacement of the spring through the first link to the second link, a second link that links the reciprocating motion of the third link
- a support portion (guide) 530 A structure in which a third link is omitted according to the structure of an existing system (FIGS. 8 and 9), a third link is omitted, a first link and a second link are combined into one (FIG. 10) (Fig. 12) instead of the role of the first link, or a form in which the first link and the second link are combined (Fig. 13).
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Abstract
Description
Claims (46)
- 제 1 대상체와 제 2 대상체 사이에 연결되어 상기 제1대상체와 제2대상체 사이의 상대운동에 의해 서로 간에 전달되는 진동을 절연시키는 메인 스프링이 구비되는 진동 절연 시스템에 추가 설치되는 진동 절연 시스템의 부강성 장치에 있어서,최초 설치시 최대로 인장되거나 또는 최대로 압축된 상태로 설치되어, 상기 제1대상체와 제2대상체의 상대운동에 따라서, 초기의 최대 인장변위 또는 최대 압축변위가 완화되는 보조 스프링을 구비한 진동 절연 시스템의 부강성 장치.
- 제1항에 있어서,상기 제1대상체와 제2대상체의 사이에 위치하며, 일단부는 상기 제1대상체의 일측면에 고정 설치되어 상기 제1대상체의 상하 움직임에 따라 함께 이동하는 링크부;상기 제1대상체와 제2대상체의 사이에 위치하며, 일단부는 상기 제2대상체의 일측면에 고정 설치되는 지지부를 더 구비하며,상기 보조 스프링은, 그 일단이 상기 링크부의 타단부에 연결되며, 그 타단은 상기 지지부의 타단부에 연결되는 것을 특징으로 하는, 진동 절연 시스템의 부강성 장치.
- 제 2 항에 있어서,상기 메인 스프링의 압축 또는 인장 변위량에 따라, 상기 메인 스프링이 갖는 포텐션에너지(Potential Energy)는 중립상태보다 증가하고, 상기 보조 스프링이 갖는 포텐셜에너지는 상기 변위량에 따라 중립상태보다 항상 감소하는 변화가 발생하도록 구비되어, 상기 진동 절연 시스템의 운동에너지에 대한 포텐셜에너지의 시간당 교환율이 감소됨으로써 상기 진동 절연 시스템의 고유진동수를 1Hz 이하인 것을 특징으로 하는 진동 절연 시스템의 부강성 장치.
- 제 2 항에 있어서,상기 보조 스프링은, 제 1 대상체 및 제 2 대상체의 상대운동 방향과 직각 방향으로 설치되는 것을 특징으로 하는 진동 절연 시스템의 부강성 장치.
- 제 2 항에 있어서,상기 링크부는,상기 제 1 대상체의 일측부에 고정되어 제 1 대상체의 움직임에 따라 함께 상하 운동을 하는 제 1 링크,상기 제1 링크의 상하 움직임을 상기 보조 스프링의 수평 변위로 변환하는 제 2 링크,제 2 링크와 연결되어, 상기 보조 스프링의 수평 왕복 변위를 가능케 하고, 상기 지지부의 일부에 의해 그 왕복 운동이 가이드되는 제 3 링크를 포함하는 것을 특징으로 하는 진동 절연 시스템의 부강성 장치.
- 제 1 대상체와 제 2 대상체 사이에 연결되어 상기 제1대상체 또는 제2대상체 사이의 상대운동에 의해 전달되는 진동을 절연시키는 메인 스프링과,상기 제 1 항 내지 제 5 항 중 어느 한 항에 기재된 진동 절연 시스템의 부강성 장치를 포함하는 진동 절연 시스템.
- 제 1 대상체에 고정 설치되는 상부레일가드;상기 상부레일가드의 하부에 위치하며 제 2 대상체에 고정 설치되는 하부레일가드;상기 상부레일가드과 하부레일가드의 사이에 연결되어 상기 하부레일가드를 중심으로 상기 상부레일가드를 상하 이동시키는 지지링크;상기 상부레일가드와 하부레일가드의 사이에 연결되거나 또는 상기 지지링크의 일측에 연결되어, 상기 제1대상체 및 제2대상체로부터 전달되는 진동을 완충시키는 메인 스프링;상기 제 2 대상체 또는 상기 하부레일가드의 상부에 고정 설치되는 지지판; 상기 지지판의 일측면에 고정 설치되며, 가이드부를 구비하는 링크하우징; 상기 가이드부에 삽입되며 상기 가이드부 내에서 슬라이딩되어 수평 왕복 이동이 가능하도록 구비되는 제3링크와, 상기 상부레일가드의 일측부에 고정되어 상기 상부레일가드의 움직임에 따라 함께 상하 이동되도록 구비되는 제1링크와, 상기 제1링크의 상하 움직임에 의해 상기 제3링크가 수평 왕복 이동되도록 상기 제3링크와 제1링크를 연결하는 제2링크를 포함하는 링크부; 및 상기 링크부의 일측에 일단부가 연결되며, 타단부는 상기 지지판의 일측에 연결되는 보조 스프링을 포함하는 부강성 장치를 구비하는 차량 운전자 의자용 진동 절연 서스펜션 시스템.
- 제 7항에 있어서,상기 보조 스프링은, 최초 설치시 최대로 인장되거나 또는 최대로 압축된 상태로 설치되어, 상기 상부레일가드 및 하부레일가드의 상대운동에 의해, 초기의 최대 인장변위 또는 최대 압축변위가 완화되도록 구비되는 것을 특징으로 하는 차량 운전자 의자용 진동 절연 서스펜션 시스템.
- 제 8 항에 있어서,상기 메인 스프링의 압축 또는 인장 변위량에 따라, 상기 메인 스프링이 갖는 포텐션에너지(Potential Energy)는 중립상태보다 증가하고, 상기 보조 스프링이 갖는 포텐셜에너지는 상기 변위량에 따라 중립상태 보다 항상 감소하는 변화가 발생하도록 구비되어, 상기 진동 절연 시스템의 운동에너지에 대한 포텐셜에너지의 시간당 교환율이 감소됨으로써 상기 진동 절연 시스템의 고유진동수를 1Hz 이하인 것을 특징으로 하는 차량 운전자 의자용 진동 절연 서스펜션 시스템.
- 제 8 항에 있어서,상기 보조 스프링은, 제 1 대상체 및 제 2 대상체의 상대운동 방향과 직각 방향으로 설치되는 것을 특징으로 하는 차량 운전자 의자용 진동 절연 서스펜션 시스템.
- 제1방향으로 상대운동하는 제1, 2대상체 사이에서 전달되는 진동을 완충시키며, 중립위치에서 포텐셜에너지가 최소가 되는 제1탄성부재;상기 제1, 2대상체의 상대운동에 따라 포텐셜에너지가 변화하는 제2탄성부재; 및상기 중립위치에서 상기 제2탄성부재의 포텐셜에너지가 최대가 되도록 상기 제1대상체와 상기 제2탄성부재를 연결하는 링크부;를 포함하는 것을 특징으로 하는 진동 절연 시스템.
- 제11항에 있어서,상기 제1, 2대상체의 상대위치가 상기 중립위치에서 변화함에 따라, 상기 제1탄성부재의 포텐셜에너지는 증가하는 것을 특징으로 하는 진동 절연 시스템.
- 제11항에 있어서,상기 제1, 2대상체의 상대위치가 상기 중립위치에서 변화함에 따라, 상기 제2탄성부재의 포텐셜에너지는 감소하는 것을 특징으로 하는 진동 절연 시스템.
- 제11항에 있어서,상기 제1, 2탄성부재의 전체 포텐셜에너지는 상기 중립위치에서 최소가 되는 것을 특징으로 하는 진동 절연 시스템.
- 제14항에 있어서,상기 제1, 2대상체의 상대위치가 상기 중립위치에서 변화함에 따라, 상기 제1, 2탄성부재의 전체 포텐셜에너지는 증가하는 것을 특징으로 하는 진동 절연 시스템.
- 제11항에 있어서,상기 제1탄성부재는 압축 스프링을 포함하는 것을 특징으로 하는 진동 절연 시스템.
- 제11항에 있어서,상기 제1탄성부재는 인장 스프링을 포함하는 것을 특징으로 하는 진동 절연 시스템.
- 제11항에 있어서,상기 제2탄성부재는 상기 중립위치에서 최대로 압축되는 압축 스프링을 포함하는 것을 특징으로 하는 진동 절연 시스템.
- 제18항에 있어서,상기 압축 스프링은 상기 제1방향과는 다른 제2방향으로 변위되는 것을 특징으로 하는 진동 절연 시스템.
- 제19항에 있어서,상기 제2방향은 상기 제1방향과 수직한 것을 특징으로 하는 진동 절연 시스템.
- 제18항에 있어서,상기 압축 스프링은 회전 가능하게 고정된 일단을 기준으로 회전하면서 변위되는 것을 특징으로 하는 진동 절연 시스템.
- 제11항에 있어서,상기 제2탄성부재는 상기 중립위치에서 최대로 인장되는 인장 스프링을 포함하는 것을 특징으로 하는 진동 절연 시스템.
- 제22항에 있어서,상기 인장 스프링은 상기 제1방향과는 다른 제2방향으로 변위되는 것을 특징으로 하는 진동 절연 시스템.
- 제23항에 있어서,상기 제2방향은 상기 제1방향과 수직한 것을 특징으로 하는 진동 절연 시스템.
- 제22항에 있어서,상기 인장 스프링은 회전 가능하게 고정된 일단을 기준으로 회전하면서 변위되는 것을 특징으로 하는 진동 절연 시스템.
- 제11항에 있어서, 상기 링크부는,상기 제1대상체에 고정되어 상기 제1방향으로 이동하는 제1링크;상기 제1링크에 연결되어 상기 제1링크의 이동방향을 상기 제2방향으로 전환하기 위한 제2링크; 및일단이 상기 제2링크에 연결되며, 타단이 상기 제2탄성부재의 일단에 연결되는 제3링크;를 포함하고,상기 제2탄성부재의 타단은 고정되는 것을 특징으로 하는 진동 절연 시스템.
- 제26항에 있어서,상기 제2방향은 상기 제1방향과 수직한 것을 특징으로 하는 진동 절연 시스템.
- 제26항에 있어서,상기 제2탄성부재는 상기 제2방향으로 변위되는 인장 스프링을 포함하고,상기 인장 스프링은 상기 중립위치에서 최대로 인장되는 것을 특징으로 하는 진동 절연 시스템.
- 제26항에 있어서,상기 제2탄성부재는 상기 제2방향으로 변위되는 압축 스프링을 포함하고,상기 압축 스프링은 상기 중립위치에서 최대로 압축되는 것을 특징으로 하는 진동 절연 시스템.
- 제11항에 있어서,상기 링크부는 상기 제1대상체에 고정되어 상기 제1방향으로 이동하는 제1링크를 포함하고,상기 제2탄성부재는 압축 스프링으로 포함하고,상기 압축 스프링의 일단은 상기 제1링크에 연결되고,상기 압축 스프링의 타단은 회전 가능하게 고정되는 것을 특징으로 하는 진동 절연 시스템.
- 제30항에 있어서,상기 압축 스프링은 상기 중립위치에서 최대로 압축되고,상기 제1, 2대상체의 상대운동에 따라, 상기 압축 스프링은 압축상태를 유지하면서 고정된 상기 압축 스프링의 상기 타단을 기준으로 회전하면서 변위되는 것을 특징으로 하는 진동 절연 시스템.
- 제11항에 있어서,상기 링크부는, 상기 제1대상체에 고정되어 상기 제1방향으로 이동하며 만곡부를 구비하는 제1링크를 포함하고,상기 제2탄성부재의 일단은 상기 제1링크의 상기 만곡부와 접하고,상기 제2탄성부재의 타단은 고정되는 것을 특징으로 하는 진동 절연 시스템.
- 제32항에 있어서,상기 제2탄성부재는 롤러를 통하여 상기 만곡부와 접하는 것을 특징으로 하는 진동 절연 시스템.
- 제32항에 있어서,상기 제2탄성부재는 압축 스프링을 포함하고,상기 제1, 2대상체의 상대운동에 따라, 상기 압축 스프링은 압축상태를 유지하면서 상기 만곡부와 접하는 것을 특징으로 하는 진동 절연 시스템.
- 제34항에 있어서,상기 만곡부는 상기 중립위치에서 상기 압축 스프링이 최대로 압축되도록 형성되는 것을 특징으로 하는 진동 절연 시스템.
- 제32항에 있어서,상기 제2탄성부재는 인장 스프링을 포함하고,상기 제1, 2대상체의 상대운동에 따라, 상기 인장 스프링은 인장상태를 유지하면서 상기 만곡부와 접하는 것을 특징으로 하는 진동 절연 시스템.
- 제36항에 있어서,상기 만곡부는 상기 중립위치에서 상기 인장 스프링이 최대로 인장되도록 형성되는 것을 특징으로 하는 진동 절연 시스템.
- 제11항에 있어서, 상기 링크부는,상기 제1대상체에 회전 가능하게 연결되는 제1링크; 및상기 제1링크와 연결되어 상기 제1, 2대상체의 상대운동에 따라 회전할 수 있도록 일단이 회전 가능하게 고정되는 제2링크;를 포함하고,상기 제2탄성부재의 일단은 상기 제2링크의 타단에 연결되며, 상기 제2탄성부재의 타단은 회전 가능하게 고정되는 것을 특징으로 하는 진동 절연 시스템.
- 제38항에 있어서,상기 제2탄성부재는 인장 스프링을 포함하고,상기 제2링크의 상기 일단은, 상기 중립위치에서 상기 인장 스프링이 최대로 인장되는 위치에 배치되는 것을 특징으로 하는 진동 절연 시스템.
- 제38항에 있어서,상기 제2탄성부재는 압축 스프링을 포함하고,상기 제2링크의 상기 일단은, 상기 중립위치에서 상기 압축 스프링이 최대로 압축되는 위치에 배치되는 것을 특징으로 하는 진동 절연 시스템.
- 제11항에 있어서,상기 제1, 2대상체 사이의 진동을 감쇄시키는 댐퍼;를 더 포함하는 것을 특징으로 하는 진동 절연 시스템.
- 제11항에 있어서,상기 제2탄성부재의 일단을 고정시키는 지지부;를 더 포함하는 것을 특징으로 하는 진동 절연 시스템.
- 제11항에 있어서,상기 진동 절연 시스템의 고유 진동수는 1Hz 이하인 것을 특징으로 하는 진동 절연 시스템.
- 제11항 내지 제43항 중 어느 한 항에 따르는 진동 절연 시스템을 포함하는 차량 운전자 의자용 진동 절연 서스펜션 시스템.
- 제11항 내지 제43항 중 어느 한 항에 따르는 진동 절연 시스템을 포함하는 자동차 서스펜션 시스템.
- 제11항 내지 제43항 중 어느 한 항에 따르는 진동 절연 시스템을 포함하는 기계 지지 시스템.
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US13/120,135 US20110278425A1 (en) | 2008-09-19 | 2009-09-17 | Vibration isolation system with a unique low vibration frequency |
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CN111336210A (zh) * | 2018-12-19 | 2020-06-26 | 中国石油大学(华东) | 一种基于负刚度和可变阻尼的混合振动控制装置、方法及应用 |
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- 2009-09-17 KR KR1020117008900A patent/KR101554717B1/ko active IP Right Grant
- 2009-09-17 US US13/120,135 patent/US20110278425A1/en not_active Abandoned
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CN107391874A (zh) * | 2017-08-07 | 2017-11-24 | 赵雷雷 | 主簧压缩式低频隔振车辆座椅悬架副簧刚度的设计方法 |
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CN111336210A (zh) * | 2018-12-19 | 2020-06-26 | 中国石油大学(华东) | 一种基于负刚度和可变阻尼的混合振动控制装置、方法及应用 |
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US20110278425A1 (en) | 2011-11-17 |
KR101554717B1 (ko) | 2015-09-21 |
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WO2010032971A3 (ko) | 2010-07-15 |
KR20110073526A (ko) | 2011-06-29 |
JP2012503159A (ja) | 2012-02-02 |
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