Multi-spring cam roller quasi-zero stiffness vibration isolation device

Abstract

The invention discloses a multi-spring cam roller quasi-zero stiffness vibration isolation device, and belongs to the technical field of vibration isolation. The multi-spring cam roller quasi-zero stiffness vibration isolation device comprises a bottom plate, a loading platform and a fork type lifting mechanism, and further comprises a first sliding rod and a second sliding rod, the supporting beam is provided with a first sliding hole, the supporting beam is slidably connected to the first sliding rod through the first sliding hole in the length direction of the first sliding rod, and one end of the supporting beam is connected with the fork type lifting mechanism; the X-direction spring is used for applying elastic force opposite to the movement direction of the supporting beam to the supporting beam; a cam; when the supporting beam slides on the first sliding rod, the supporting beam drives the spring telescopic mechanism to stretch out and draw back through the cam. According to the multi-spring cam roller quasi-zero stiffness vibration isolation device, the stiffness of the whole vibration isolation device is reduced, the inherent frequency of the whole vibration isolation device is reduced, the good bearing capacity is kept, and low-frequency vibration of a transported object can be effectively isolated.

Description

Technical Field

[0001] The invention relates to the technical field of vibration isolation, and in particular to a multi-spring cam roller quasi-zero stiffness vibration isolation device. Background Art

[0002] The vibrations generated by vehicles during transportation are mostly low-frequency vibrations, while the effective vibration isolation frequency of traditional linear vibration isolators is medium and high frequency. Reducing the stiffness of the vibration isolation system will reduce the natural frequency of the system, thereby widening the vibration isolation frequency band and improving the overall vibration isolation effect. Although this widens the frequency band, it also brings about the problem of low stiffness and reduced load-bearing capacity. Therefore, a quasi-zero stiffness vibration isolator is proposed. It is widely used due to its wide vibration isolation frequency band and good load-bearing capacity. Compared with traditional vibration isolators, the design of the negative stiffness structure is the most important part of this method. At present, scholars at home and abroad have designed a variety of structures to achieve negative stiffness.

[0003] The negative stiffness elements formed by mechanical springs are relatively simple and classic. There are also relatively complex negative stiffness mechanisms formed by other types of springs, such as canted springs. The quasi-zero stiffness device formed by canted springs has the characteristics of low cost, strong adaptability to complex environments, simple structure, long service life and easy design; butterfly springs are widely used in industry; air springs and magnetic springs have the advantages of small size, light weight, material saving, good stability, low vibration and noise, and strong flexibility, and are increasingly widely used in the industrial field.

[0004] However, the above-disclosed quasi-zero stiffness vibration isolation and negative stiffness mechanism selection cannot simultaneously meet the performance of good bearing capacity and good low-frequency vibration isolation, and the flexibility and multi-directivity are poor. Summary of the invention

[0005] The purpose of the present invention is to overcome the problems of flexibility and multi-directivity in the prior art, and to provide a multi-spring cam roller quasi-zero stiffness vibration isolation device, which not only reduces the stiffness of the entire vibration isolation device and reduces the natural frequency of the entire vibration isolation device to broaden the vibration isolation frequency band, but also retains good load-bearing capacity, and can effectively isolate the low-frequency vibration of the transported object during vehicle transportation.

[0006] The present invention provides a multi-spring cam roller quasi-zero stiffness vibration isolation device, comprising a base plate, a loading platform and a fork-type lifting mechanism, wherein the fork-type lifting mechanism is connected to the base plate, the loading platform is connected to the fork-type lifting mechanism, and further comprising:

[0007] A first sliding bar, disposed on the bottom plate;

[0008] A support beam is provided with a first sliding hole, the support beam is slidably connected to the first sliding rod through the first sliding hole, one end of the support beam is connected to the fork lifting mechanism, and when the loading platform moves in the vertical direction, the fork lifting mechanism drives the support beam to slide on the first sliding rod;

[0009] An X-direction spring, provided on the first slide bar, one end of the X-direction spring abutting against the support beam, and the X-direction spring is used to apply an elastic force to the support beam in a direction opposite to the movement direction of the support beam;

[0010] A cam is arranged on one side of the support beam;

[0011] The spring telescopic mechanism abuts against the outer edge of the cam, the telescopic direction of the spring telescopic mechanism is perpendicular to the length direction of the first slide bar, the stiffness of the spring telescopic mechanism is smaller than the stiffness of the X-direction spring, and when the support beam slides on the first slide bar, the support beam drives the spring telescopic mechanism to telescope through the cam.

[0012] Preferably, the spring telescopic mechanism includes a guide rail, a stopper, a first slider and a Y-direction spring, the guide rail is arranged on the base plate, the length direction of the guide rail is perpendicular to the length direction of the first slide bar, the stopper is arranged at one end of the guide rail, the first slider is slidably connected to the other end of the guide rail, one end of the Y-direction spring abuts against the stopper, and the other end of the Y-direction spring abuts against the first slider, the Y-direction spring is used to apply an elastic force toward one side of the cam to the first slider, and under the action of the elastic force of the Y-direction spring, the first slider abuts against the outer edge of the cam.

[0013] Preferably, the fork lifting mechanism includes a first connecting rod, a second connecting rod, a first sliding mechanism and a second sliding mechanism, the middle part of the first connecting rod is hinged to the middle part of the second connecting rod, the top end of the first connecting rod is hinged to the loading platform, the bottom end of the first connecting rod is connected to the first sliding mechanism, the first sliding mechanism is arranged on the bottom plate, the support beam abuts against the bottom end of the second connecting rod, the top end of the second connecting rod is connected to the second sliding mechanism, the bottom end of the second connecting rod is hinged to the bottom plate, the second sliding mechanism is arranged on the bottom plate, and the sliding directions of the first sliding mechanism and the second sliding mechanism are both along the length direction of the first sliding rod.

[0014] Preferably, the first sliding mechanism and the second sliding mechanism have the same structure, both comprising a second sliding rod and a second slider, the second sliding rod being arranged on the bottom plate, the length direction of the second sliding rod being in the same direction as the length direction of the first sliding rod, the second slider being slidably connected to the second sliding rod, the second slider being hinged to the bottom end of the first connecting rod or the top end of the second connecting rod, and the bottom end of the first connecting rod being abutted against the support beam through the second slider.

[0015] Preferably, an energy dissipation mechanism is further provided between the stopper and the first slider, the energy dissipation mechanism comprising a cylinder body and a piston, the cylinder body is connected to the stopper, the piston is slidably connected to the inner cavity of the cylinder body along the length direction of the guide rail, the piston is connected to the first slider, the Y-direction spring is arranged outside the cylinder body, the side wall of the cylinder body is provided with a first through hole, and the inner cavity of the cylinder body is connected to the atmosphere through the first through hole.

[0016] Preferably, a valve body is provided in the first through hole, a magnet is provided in the valve body, a first sliding hole is provided in the valve body, an armature is slidably connected in the first sliding hole, one end of the armature is attracted to the magnet, a second through hole is provided on the magnet, a third through hole is provided on the armature, the inner diameter of the third through hole is smaller than the second through hole, the inner cavity of the cylinder body is connected to the atmosphere through the second through hole and the third through hole, a ventilation groove is provided on the inner wall of the first sliding hole, the ventilation groove is connected to the atmosphere, and when the armature is out of contact with the magnet, the second through hole is connected to the third through hole and the ventilation groove at the same time.

[0017] Preferably, a plurality of spoiler blocks are provided in the third through hole, and the spoiler blocks are used to increase the resistance of gas when passing through the third through hole.

[0018] Preferably, a third slide bar is provided on the bottom plate, the third slide bar is arranged parallel to the first slide bar, a second slide hole is provided on the support beam, and the support beam is slidably connected to the third slide bar through the second slide hole.

[0019] Preferably, a roller is provided on the first sliding block, and an outer edge of the roller abuts against an outer edge of the cam.

[0020] Preferably, the position of the stopper on the guide rail is adjustable.

[0021] Compared with the prior art, the beneficial effects of the present invention are as follows: a multi-spring cam roller quasi-zero stiffness vibration isolation device of the present invention applies an elastic force in the opposite direction of the movement of the support beam to the support beam through the X-direction spring, thereby applying a reverse supporting force to the object on the loading platform; since the stiffness of the X-direction spring is relatively large, under the action of the elastic force of the X-direction spring, the entire vibration isolation device has a relatively large load-bearing capacity; when the carried object vibrates on the loading platform, the vibration will cause the loading platform to move in the vertical direction; under the action of the fork-type lifting mechanism, the support frame will be driven to slide on the first slide bar along the length direction of the first slide bar; the support frame drives the cam to move along the length direction of the first slide bar; under the action of the cam, the spring telescopic mechanism reciprocates along its own length direction, and the stiffness of the spring telescopic mechanism is relatively small, so that the natural frequency of the entire vibration isolation device is reduced, thereby widening the vibration isolation frequency band, and can effectively improve the vibration isolation effect of the entire vibration isolation device.

[0022] The spring expansion and contraction mechanism of the vibration isolation device causes the Y-direction spring to be compressed back and forth when the cam reciprocates along the length direction of the first slide bar. The stiffness of the Y-direction spring is relatively small. Therefore, under the buffering effect of the Y-direction spring, the low-frequency vibration of the object on the loading platform can be effectively suppressed. When the loading platform reciprocates in the vertical direction, the bottom end of the first connecting rod drives the second slider of the first sliding mechanism to slide on the second slide bar of the first sliding mechanism. Since the length direction of the second slide bar is in the same direction as the length direction of the first slide bar, the second slide bar can guide the first slide bar, which can prevent the loading platform from twisting during vibration, thereby preventing the object on the loading platform from tipping over and ensuring the stability of object transportation. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 It is a schematic diagram of the top view structure of the present invention;

[0024] Figure 2 It is a schematic diagram of the main cross-sectional structure of the present invention;

[0025] Figure 3 It is a structural schematic diagram of the AA surface of the present invention;

[0026] Figure 4 It is a structural schematic diagram of the spring telescopic mechanism of the present invention;

[0027] Figure 5 It is a schematic diagram of the structure in the valve body of the present invention;

[0028] Figure 6 It is a structural schematic diagram of the BB surface of the present invention;

[0029] Figure 7 It is a structural schematic diagram of the present invention in an initial state;

[0030] Figure 8 It is a schematic diagram of the structure of the present invention in a balanced state;

[0031] Fig. 9 It is a schematic diagram of the structure of the present invention in a critical state;

[0032] Fig.10 It is a schematic diagram of the structure of the present invention under a stress state;

[0033] Fig.11 This is a dynamic response diagram under displacement excitation in the first state of the present invention;

[0034] Fig.12 This is a dynamic response diagram under displacement excitation in the second state of the present invention;

[0035] Fig.13 This is a dynamic response diagram under displacement excitation in the third state of the present invention;

[0036] Fig.14 This is the dynamic response diagram under displacement excitation in the fourth state of the present invention.

[0037] Description of reference numerals:

[0038] 101. base plate, 102. loading platform, 103. fork lift mechanism, 104. first slide bar, 105. support beam, 106. X-direction spring, 107. cam, 108. spring telescopic mechanism, 201. guide rail, 202. block, 203. first slider, 204. Y-direction spring, 301. first connecting rod, 302. second connecting rod, 303. first sliding mechanism, 304. second sliding mechanism, 4. roller, 501. second slide bar, 502. second slider, 601. cylinder body, 602. piston, 701. magnet, 702. first slide hole, 703. armature, 704. second through hole, 705. third through hole, 706. ventilation groove, 707. valve body, 8. spoiler, 9. third slide bar. DETAILED DESCRIPTION

[0039] The following is combined with Figure 1-Figure 14 , the specific implementation of the present invention is described in detail, but it should be understood that the protection scope of the present invention is not limited by the specific implementation. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of the present invention.

[0040] like Figure 1-Figure 14As shown, the multi-spring cam roller quasi-zero stiffness vibration isolation device provided by the present invention includes a base plate 101, a loading platform 102 and a fork lifting mechanism 103, wherein the fork lifting mechanism 103 is connected to the base plate 101, and the loading platform 102 is connected to the fork lifting mechanism 103, and further includes: a first slide bar 104, a support beam 105, an X-direction spring 106, a cam 107 and a spring expansion and contraction mechanism 108, wherein the first slide bar 104 is arranged on the base plate 101; the support beam 105 is provided with a first slide hole 702, wherein the support beam 105 is slidably connected to the first slide bar 104 through the first slide hole 702, and one end of the support beam 105 is connected to the fork lifting mechanism 103, and when the loading platform 102 moves in the vertical direction, The fork lifting mechanism 103 drives the support beam 105 to slide on the first slide bar 104; the X-direction spring 106 is arranged on the first slide bar 104, and one end of the X-direction spring 106 abuts against the support beam 105, and the X-direction spring 106 is used to apply an elastic force to the support beam 105 that is opposite to the movement direction of the support beam 105; the cam 107 is arranged on one side of the support beam 105; the spring expansion and contraction mechanism 108 abuts against the outer edge of the cam 107, and the expansion and contraction direction of the spring expansion and contraction mechanism 108 is perpendicular to the length direction of the first slide bar 104, and the stiffness of the spring expansion and contraction mechanism 108 is less than the stiffness of the X-direction spring 106. When the support beam 105 slides on the first slide bar 104, the support beam 105 drives the spring expansion and contraction mechanism 108 to expand and contract through the cam 107.

[0041] The working principle of the above embodiment is briefly described:

[0042] When the device is in use, the base plate 101 is fixed on the transport vehicle, and then the carried object is placed on the loading platform 102. The gravity of the object will press down the loading platform 102, so that the fork lifting mechanism 103 is compressed. When the fork lifting mechanism 103 is compressed, the fork lifting mechanism 103 drives the support beam 105 to slide on the first slide bar 104. Since one end of the X-direction spring 106 abuts against the support beam 105, the X-direction spring 106 applies an elastic force to the support beam 105 in the opposite direction of the movement of the support beam 105, thereby applying a reverse supporting force to the object on the loading platform 102. Since the stiffness of the X-direction spring 106 is relatively large, under the action of the elastic force of the X-direction spring 106, the entire vibration isolation device has a large load-bearing capacity. When the carried object vibrates on the loading platform 102, the vibration will cause the loading platform 102 to move in the vertical direction. Similarly, under the action of the fork-type lifting mechanism 103, the support frame will be driven to slide on the first slide bar 104 along the length direction of the first slide bar 104, and the support frame will drive the cam 107 to move along the length direction of the first slide bar 104. Since one end of the spring expansion and contraction mechanism 108 abuts against the outer edge of the cam 107, and the expansion and contraction direction of the spring expansion and contraction mechanism 108 is perpendicular to the length direction of the first slide bar 104, under the action of the cam 107, the spring expansion and contraction mechanism 108 reciprocates along its own length direction, and the stiffness of the spring expansion and contraction mechanism 108 is relatively small, which reduces the natural frequency of the entire vibration isolation device, thereby widening the vibration isolation frequency band, and can effectively improve the vibration isolation effect of the entire vibration isolation device.

[0043] The multi-spring cam roller quasi-zero stiffness vibration isolation device of the present invention not only reduces the stiffness of the entire vibration isolation device to reduce the natural frequency of the entire vibration isolation device to broaden the vibration isolation frequency band, but also retains a good load-bearing capacity and can effectively isolate the low-frequency vibration of the transported object during vehicle transportation.

[0044] On the basis of the above embodiments, in order to effectively suppress the low-frequency vibration of the loading platform 102 .

[0045] like Figure 1-Figure 5 As shown, the spring expansion and contraction mechanism 108 includes a guide rail 201, a stopper 202, a first slider 203 and a Y-direction spring 204. The guide rail 201 is arranged on the base plate 101, and the length direction of the guide rail 201 is perpendicular to the length direction of the first slide bar 104. The stopper 202 is arranged at one end of the guide rail 201, and the first slider 203 is slidably connected to the other end of the guide rail 201. One end of the Y-direction spring 204 abuts against the stopper 202, and the other end of the Y-direction spring 204 abuts against the first slider 203. The Y-direction spring 204 is used to apply an elastic force to the first slider 203 toward one side of the cam 107. Under the action of the elastic force of the Y-direction spring 204, the first slider 203 abuts against the outer edge of the cam 107.

[0046] When the cam 107 reciprocates along the length direction of the first slide bar 104, the cam 107 drives the first slider 203 to reciprocate along the length direction perpendicular to the first slide bar 104, that is, the length direction of the guide rail 201, and the distance between the first slider 203 and the stop block 202 changes reciprocatingly. Since one end of the Y-direction spring 204 abuts against the stop block 202, and the other end of the Y-direction spring 204 abuts against the first slider 203, the Y-direction spring 204 is reciprocatingly compressed, and the stiffness of the Y-direction spring 204 is relatively small. Therefore, under the buffering effect of the Y-direction spring 204, the low-frequency vibration of the object on the loading platform 102 can be effectively suppressed.

[0047] As a preferred solution, Figure 2 and Figure 3 As shown, the fork lifting mechanism 103 includes a first link 301, a second link 302, a first sliding mechanism 303 and a second sliding mechanism 304, the middle part of the first link 301 is hinged to the middle part of the second link 302, the top end of the first link 301 is hinged to the loading platform 102, the bottom end of the first link 301 is connected to the first sliding mechanism 303, the first sliding mechanism 303 is arranged on the bottom plate 101, the support beam 105 is abutted against the bottom end of the second link 302, the top end of the second link 302 is connected to the second sliding mechanism 304, the bottom end of the second link 302 is hinged to the bottom plate 101, the second sliding mechanism 304 is arranged on the bottom plate 101, and the sliding directions of the first sliding mechanism 303 and the second sliding mechanism 304 are both along the length direction of the first sliding rod 104. When the loading platform 102 reciprocates in the vertical direction, the loading platform 102 drives the first connecting rod 301 hinged thereto to rotate, the first connecting rod 301 drives the second connecting rod 302 to rotate, the first connecting rod 301 drives the first sliding mechanism 303 to slide, and the second connecting rod 302 drives the second sliding mechanism 304 to slide. When the first connecting rod 301 drives the first sliding mechanism 303 to slide, since the sliding directions of the first sliding mechanism 303 and the second sliding mechanism 304 are the same as the length direction of the first sliding rod 104, the first connecting rod 301 can drive the support beam 105 abutting therewith to reciprocate along the length direction of the first sliding rod 104. Under the buffering of the Y-direction spring 204, the low-frequency vibration of the object on the loading platform 102 can be effectively suppressed.

[0048] As a preferred solution, Figure 2 and Figure 3As shown, the first sliding mechanism 303 and the second sliding mechanism 304 have the same structure, both including a second sliding bar 501 and a second slider 502, the second sliding bar 501 is arranged on the bottom plate 101, the length direction of the second sliding bar 501 is in the same direction as the length direction of the first sliding bar 104, the second slider 502 is slidably connected to the second sliding bar 501, the second slider 502 is hinged to the bottom end of the first connecting rod 301 or the top end of the second connecting rod 302, and the bottom end of the first connecting rod 301 is abutted against the support beam 105 through the second slider 502. When the loading platform 102 reciprocates in the vertical direction, it drives the first connecting rod 301 to rotate reciprocatingly. Since the top end of the first connecting rod 301 is hinged to the loading platform 102, the first connecting rod 301 is hinged to the second connecting rod 302, and the top end of the second connecting rod 302 is hinged to the loading platform 102, therefore, when the loading platform 102 reciprocates in the vertical direction, the bottom end of the first connecting rod 301 drives the second slider 502 of the first sliding mechanism 303 to slide on the second sliding rod 501 of the first sliding mechanism 303. Since the length direction of the second sliding rod 501 is in the same direction as the length direction of the first sliding rod 104, the second sliding rod 501 can guide the first sliding rod 104, and can prevent the loading platform 102 from twisting during vibration, thereby preventing objects on the loading platform 102 from overturning, thereby ensuring the stability of object transportation.

[0049] As a preferred solution, Figure 1 and Figure 3-Figure 5 As shown, an energy dissipation mechanism is also provided between the stopper 202 and the first slider 203, and the energy dissipation mechanism includes a cylinder 601 and a piston 602, the cylinder 601 is connected to the stopper 202, the piston 602 is slidably connected to the inner cavity of the cylinder 601 along the length direction of the guide rail 201, the piston 602 is connected to the first slider 203, the Y-direction spring 204 is provided outside the cylinder 601, and the side wall of the cylinder 601 is provided with a first through hole, and the inner cavity of the cylinder 601 is connected to the atmosphere through the first through hole. By setting an energy dissipation mechanism, when the distance between the first slider 203 and the stopper 202 changes back and forth, the Y-direction spring 204 buffers the vibration of the first slider 203 while the first slider 203 drives the piston 602 to reciprocate in the cylinder 601, thereby causing the volume of the inner cavity of the cylinder 601 to change back and forth. Since the inner cavity of the cylinder 601 is connected to the atmosphere through the first through hole, the inner cavity of the cylinder 601 is reciprocatedly inflated or exhausted. Since the airflow has a certain viscosity, the airflow will produce a certain resistance to the flow of the airflow when passing through the first through hole, and there is a certain friction between the piston 602 and the inner wall of the cylinder 601. The combined effect of the two can greatly consume the kinetic energy of the vibration of the piston 602, thereby consuming the kinetic energy of the first slider 203 during vibration, and enhancing the suppression effect of the entire vibration isolation device on low-frequency vibration.

[0050] As a preferred solution, Figure 1 and Figure 3-Figure 6 As shown, a valve body 707 is provided in the first through hole, a magnet 701 is provided in the valve body 707, a first sliding hole 702 is provided in the valve body 707, an armature 703 is slidably connected in the first sliding hole 702, one end of the armature 703 is attracted to the magnet 701, a second through hole 704 is provided on the magnet 701, a third through hole 705 is provided on the armature 703, the inner diameter of the third through hole 705 is smaller than the second through hole 704, the inner cavity of the cylinder body 601 is connected to the atmosphere through the second through hole 704 and the third through hole 705, a ventilation groove 706 is provided on the inner wall of the first sliding hole 702, and the ventilation groove 706 is connected to the atmosphere, when the armature 703 is out of contact with the magnet 701, the second through hole 704 is connected to the third through hole 705 and the ventilation groove 706 at the same time. By setting the valve body 707, when the loading platform 102 undergoes low-frequency vibration, under the action of the cam 107, the volume of the inner cavity of the cylinder body 601 changes slowly back and forth. Since one end of the armature 703 is attracted to the magnet 701, the gas in the inner cavity of the cylinder body 601 flows back and forth in the second through hole 704 on the cylinder body 601 and the third through hole 705 on the armature 703. Since the inner diameter of the third through hole 705 is smaller than that of the second through hole 704, the connectivity between the inner cavity of the cylinder body 601 and the atmosphere is relatively small. The third through hole 705 can hinder the flow of gas, thereby suppressing the low-frequency vibration of the loading platform 102. When the loading platform 102 vibrates at high frequency, the volume of the inner cavity of the cylinder body 601 changes back and forth rapidly. At this time, the air pressure in the inner cavity of the cylinder body 601 increases. When the airflow passes through the third through hole 705, the resistance applied by the third through hole 705 to the airflow, that is, the thrust applied by the airflow to the armature 703 increases until the airflow pushes the armature 703 away from the magnet 701. The second through hole 704 is connected to the third through hole 705 and the ventilation groove 706 at the same time. The inner cavity of the cylinder body 601 has a large degree of connectivity with the atmosphere, thereby preventing the cylinder body 601 and the piston 602 from being damaged due to excessive impact force when the loading platform 102 vibrates at high frequency.

[0051] As a preferred solution, Figure 5 and Figure 6 As shown, a plurality of spoiler blocks 8 are provided in the third through hole 705, and the spoiler blocks 8 are used to increase the resistance of the gas when passing through the third through hole 705. By providing a plurality of spoiler blocks 8, the resistance of the gas when passing through the third through hole 705 can be increased, thereby improving the energy dissipation effect of the entire energy dissipation mechanism, thereby improving the suppression effect of the vibration isolation device on the low-frequency vibration of the object on the loading platform 102.

[0052] As a preferred solution, Figure 1 and Figure 3As shown, the bottom plate 101 is provided with a third slide bar 9, the third slide bar 9 is arranged parallel to the first slide bar 104, the support beam 105 is provided with a second slide hole, and the support beam 105 is slidably connected to the third slide bar 9 through the second slide hole. By providing the third slide bar 9, the vibration of the support beam 105 is guided by the third slide bar 9, thereby ensuring the stability of the movement of the support beam 105.

[0053] As a preferred solution, Figure 1 , Figure 3 and Figure 4 As shown, the first slider 203 is provided with a roller 4, and the outer edge of the roller 4 abuts against the outer edge of the cam 107. By providing the roller 4, the friction between the first slider 203 and the cam 107 can be reduced, thereby reducing the wear of the entire vibration isolation device and ensuring the long-term stable operation of the entire vibration isolation device.

[0054] As a preferred solution, Figure 1 and Figure 3 As shown, the position of the stopper 202 on the guide rail 201 is adjustable. Since the position of the stopper 202 of the vibration isolation device on the guide rail 201 is adjustable, the pre-compression amount of the Y-direction spring 204 is adjustable, so that the vibration isolation device has a better suppression effect on low-frequency vibration.

[0055] The radius of the cam 107 is r1, and the radius of the roller 4 is r2. Figure 7 The figure shows the state when there is no object to be isolated. Figure 8 As shown, when the mass of the object to be isolated carried by the loading platform 102 is m, the vibration isolation device is in a static equilibrium position, and the stiffness of the Y-direction spring and the X-direction spring are 2K respectively. h and K v , the nonlinear stiffness of the Y-direction spring is At this time, the pre-compression amount of the negative stiffness force provided by the Y-direction spring is Δ0, and the compression length of the X-direction spring is Δ v =Mg / K v .like Fig. 9 As shown, the cam 107 of the vibration isolation device is in a disengaged critical position from the roller 4 and no longer provides negative stiffness.

[0056] like Fig.10 As shown, when the loading platform 102 is acted upon by a force, the point where the cam 107 and the roller 4 are aligned is taken as the equilibrium point, and the distance that the roller 4 moves away from this point is defined as X. When |X|<X0, the roller 4 rolls along the cam 107, generating a negative stiffness force converted to the X direction; when |X|>X0, the two wheels are separated, F v =0; when |X|=X0, the critical value X0 can be expressed as:

[0057]

[0058] When in a balanced state, the centers of the cam 107 and the roller 4 are aligned on the same horizontal line, and at this moment, the static support force of the vibration isolation device is only borne by the X-direction spring 106. During the vibration isolation process of the quasi-zero stiffness vibration isolation device, the positive stiffness of the X-direction spring 106 is balanced by the negative stiffness generated by the negative stiffness structure of the spring expansion mechanism 108, which not only reduces the overall stiffness of the vibration isolation device, but also reduces the natural frequency of the vibration isolation device, thereby expanding the frequency range of the vibration isolation effect, and cooperates with the scissor-type structure to increase the good bearing capacity.

[0059] The influence of nonlinear coefficient, excitation amplitude, and X-axis and Y-axis damping on the response amplitude of the quasi-zero stiffness vibration isolation device under base displacement excitation is analyzed.

[0060] from Fig.11 As shown in , a lower nonlinear coefficient leads to a decrease in the resonant frequency and peak value, while an increase in the nonlinear coefficient increases the peak value of the response amplitude and pushes up the resonant frequency, but the high-frequency response remains unchanged. Fig.12 As shown in the figure, when the base displacement excitation amplitude decreases, the peak value of the response amplitude and its corresponding frequency decrease. On the contrary, a larger excitation amplitude induces resonance, and when the amplitude continues to increase, the resonance frequency and peak value increase significantly. Fig.13 As shown in the figure, as the X-axis damping increases, the resonance peak and the low-frequency response amplitude decrease; while the larger Y-axis damping avoids the resonance phenomenon. Fig.14 As shown, increasing the Y-axis damping can effectively reduce the response amplitude in the resonance zone until the peak disappears, indicating that properly controlling the excitation amplitude and increasing the damping can suppress the dynamic response amplitude, thereby better suppressing low-frequency vibration.

[0061] While the embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that many changes, modifications, substitutions and variations can be made to the embodiments without departing from the principles and spirit of the invention.

Claims

1. A multi-spring cam roller quasi-zero stiffness vibration isolation device, comprising a base plate (101), a loading platform (102) and a fork-type lifting mechanism (103), wherein the fork-type lifting mechanism (103) is connected to the base plate (101), and the loading platform (102) is connected to the fork-type lifting mechanism (103), characterized in that: Also includes: A first sliding bar (104) is disposed on the bottom plate (101); A support beam (105) is provided with a first sliding hole (702), and the support beam (105) is slidably connected to the first sliding rod (104) through the first sliding hole (702). One end of the support beam (105) is connected to the fork-type lifting mechanism (103). When the loading platform (102) moves in the vertical direction, the fork-type lifting mechanism (103) drives the support beam (105) to slide on the first sliding rod (104); An X-direction spring (106) is arranged on the first sliding rod (104), one end of the X-direction spring (106) is in contact with the support beam (105), and the X-direction spring (106) is used to apply an elastic force to the support beam (105) in a direction opposite to the movement direction of the support beam (105); A cam (107) is arranged on one side of the support beam (105); The spring telescopic mechanism (108) is in contact with the outer edge of the cam (107). The telescopic direction of the spring telescopic mechanism (108) is perpendicular to the length direction of the first slide bar (104). When the support beam (105) slides on the first slide bar (104), the support beam (105) drives the spring telescopic mechanism (108) to telescope through the cam (107).

2. The multi-spring cam roller quasi-zero stiffness vibration isolation device according to claim 1, characterized in that: The spring expansion and contraction mechanism (108) comprises a guide rail (201), a stopper (202), a first slider (203) and a Y-direction spring (204); the guide rail (201) is arranged on the bottom plate (101); the length direction of the guide rail (201) is perpendicular to the length direction of the first slider (104); the stopper (202) is arranged at one end of the guide rail (201); the first slider (203) is slidably connected to the other end of the guide rail (201); one end of the Y-direction spring (204) abuts against the stopper (202); the other end of the Y-direction spring (204) abuts against the first slider (203); the Y-direction spring (204) is used to apply an elastic force toward one side of the cam (107) to the first slider (203); under the action of the elastic force of the Y-direction spring (204), the first slider (203) abuts against the outer edge of the cam (107).

3. The multi-spring cam roller quasi-zero stiffness vibration isolation device according to claim 2, characterized in that: The fork lift mechanism (103) comprises a first connecting rod (301), a second connecting rod (302), a first sliding mechanism (303) and a second sliding mechanism (304); the middle part of the first connecting rod (301) is hinged to the middle part of the second connecting rod (302); the top end of the first connecting rod (301) is hinged to the loading platform (102); the bottom end of the first connecting rod (301) is connected to the first sliding mechanism (303); the first sliding mechanism (303) is provided On the bottom plate (101), the support beam (105) is in contact with the bottom end of the second connecting rod (302), the top end of the second connecting rod (302) is connected to the second sliding mechanism (304), the bottom end of the second connecting rod (302) is hinged to the bottom plate (101), the second sliding mechanism (304) is arranged on the bottom plate (101), and the sliding directions of the first sliding mechanism (303) and the second sliding mechanism (304) are both along the length direction of the first sliding rod (104).

4. The multi-spring cam roller quasi-zero stiffness vibration isolation device according to claim 3, characterized in that: The first sliding mechanism (303) and the second sliding mechanism (304) have the same structure, and both include a second sliding bar (501) and a second slider (502). The second sliding bar (501) is arranged on the bottom plate (101). The length direction of the second sliding bar (501) is in the same direction as the length direction of the first sliding bar (104). The second slider (502) is slidably connected to the second sliding bar (501). The second slider (502) is hinged to the bottom end of the first connecting rod (301) or the top end of the second connecting rod (302). The bottom end of the first connecting rod (301) is abutted against the support beam (105) through the second slider (502).

5. The multi-spring cam roller quasi-zero stiffness vibration isolation device according to claim 2, characterized in that: An energy dissipation mechanism is also provided between the stopper (202) and the first slider (203), and the energy dissipation mechanism comprises a cylinder (601) and a piston (602). The cylinder (601) is connected to the stopper (202), and the piston (602) is slidably connected to the inner cavity of the cylinder (601) along the length direction of the guide rail (201). The piston (602) is connected to the first slider (203), and the Y-direction spring (204) is provided outside the cylinder (601). A first through hole is provided on the side wall of the cylinder (601), and the inner cavity of the cylinder (601) is connected to the atmosphere through the first through hole.

6. The multi-spring cam roller quasi-zero stiffness vibration isolation device according to claim 5, characterized in that: A valve body (707) is provided in the first through hole, a magnet (701) is provided in the valve body (707), a first sliding hole (702) is provided in the valve body (707), an armature (703) is slidably connected in the first sliding hole (702), one end of the armature (703) is attracted to the magnet (701), a second through hole (704) is provided on the magnet (701), a third through hole (705) is provided on the armature (703), and the third through hole (705) is provided on the magnet (701). 05) has an inner diameter smaller than that of the second through hole (704); the inner cavity of the cylinder body (601) is connected to the atmosphere through the second through hole (704) and the third through hole (705); a ventilation groove (706) is provided on the inner wall of the first sliding hole (702); the ventilation groove (706) is connected to the atmosphere; when the armature (703) is out of contact with the magnet (701), the second through hole (704) is connected to the third through hole (705) and the ventilation groove (706) at the same time.

7. The multi-spring cam roller quasi-zero stiffness vibration isolation device according to claim 6, characterized in that: A plurality of spoiler blocks (8) are arranged in the third through hole (705), and the spoiler blocks (8) are used to increase the resistance of gas when passing through the third through hole (705).

8. The multi-spring cam roller quasi-zero stiffness vibration isolation device according to claim 1, characterized in that: A third sliding bar (9) is provided on the bottom plate (101), and the third sliding bar (9) is arranged parallel to the first sliding bar (104). A second sliding hole is provided on the support beam (105), and the support beam (105) is slidably connected to the third sliding bar (9) through the second sliding hole.

9. The multi-spring cam roller quasi-zero stiffness vibration isolation device according to claim 2, characterized in that: A roller (4) is provided on the first sliding block (203), and the outer edge of the roller (4) abuts against the outer edge of the cam (107).

10. The multi-spring cam roller quasi-zero stiffness vibration isolation device according to claim 2, characterized in that: The position of the stopper (202) on the guide rail (201) is adjustable.

Images