CN105546026A - Low-frequency three-dimensional vibration-isolating mining dump vehicle seat based on magnetic negative-stiffness spring design - Google Patents
Low-frequency three-dimensional vibration-isolating mining dump vehicle seat based on magnetic negative-stiffness spring design Download PDFInfo
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- CN105546026A CN105546026A CN201510989738.XA CN201510989738A CN105546026A CN 105546026 A CN105546026 A CN 105546026A CN 201510989738 A CN201510989738 A CN 201510989738A CN 105546026 A CN105546026 A CN 105546026A
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- seat
- cylinder barrel
- scissors suspension
- vibration isolation
- spring
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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
- F16F15/023—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 fluid means
- F16F15/0232—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 fluid means with at least one gas spring
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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
- F16F15/022—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 dampers and springs in combination
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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
- F16F15/08—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 rubber springs ; with springs made of rubber and metal
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The invention discloses a low-frequency three-dimensional vibration-isolating vehicle seat based on a magnetic negative-stiffness spring design, and aims to solve the problem that a common car seat cannot isolate low-frequency vibrations in a horizontal direction. The low-frequency three-dimensional vibration-isolating vehicle seat comprises a vertical vibration-isolating part and a horizontal vibration-isolating part, wherein the vertical vibration-isolating part comprises a shear type suspension and a zero-stiffness magnetic damper; the shear type suspension comprises a hinged type link mechanism which is connected between a shear type suspension upper part and a shear type suspension lower part; the two ends of the zero-stiffness magnetic damper are separately positioned on the shear type suspension upper part and the shear type suspension lower part; the horizontal vibration-isolating part comprises an upper plate, a rubber damping spring seat, a primary magnet set, an outer magnet set and a seat fixing frame; when the seat bears the vibrations in the horizontal direction, a seat plate connecting plate horizontally vibrates, so that a rubber damping spring horizontally vibrates while a magnet on a bottom plate vibrates relatively; by virtue of the acting force of the rubber spring and a magnetic negative-stiffness spring to the upper plate, the upper plate is kept to have relatively small vibration displacement, and therefore, vibrations in the horizontal direction are isolated.
Description
Technical field
The invention belongs to automobiles chair art, be specifically related to a kind of low frequency three-dimensional isolation automotive seat based on the design of magnetic force Negative stiffness spring being applied to quarry tipper.
Background technique
Along with the development of automobile industry, propose requirements at the higher level to vehicle ride comfort, automotive seat affects one of driver's key factor, and quarry tipper common adopts mine car as a kind of, its driving road is rugged mine road, riving condition very severe.Quarry tipper driver due to long operating conditions severe, generally do not have on the seat of vibration isolating effect if rided in, the probability that the organ such as backbone and stomach comes to harm increases greatly relative to the driver of other vehicles.Due to man-machine system and the complexity thereof of quarry tipper, therefore the travelling comfort improving driver is the comprehensive adjustment of links anti-vibration performance, as the seat directly contacted with driver's buttocks and waist, its Security and comfort level are vital for the health of driver.The vibration isolation technique of its seat is also one of key areas of research both at home and abroad.
At present, the seat vibration isolation way of traditional quarry tipper is passive vibration isolation and half active vibration isolation.Its making method installs shock-absorbing spring in the bottom of seat, the shortcoming of the vibration isolating method of such seat is that spring rate is selected and problem of aging makes the vibration isolating effect of seat satisfactory not to the utmost, even sometimes can play the effect of amplifying vibration, this kind of vibration isolating method in addition mainly for be the vibration isolating effect of vertical direction, vibration isolating effect is not had to left and right and fore-and-aft direction, and operating mode is complicated in actual quarry tipper running process, be subject to the effect of non-coplanar force, not only be subject to the effect of the power of vertical direction, and the vibration of left and right and fore-and-aft direction, wherein the vibration of left and right and fore-and-aft direction not only affects the healthy of driver, and the operational stability of driver can be affected.In sum, for quarry tipper develop a kind of multidimensional, nonlinear isolation seat is very important.
Summary of the invention
For above defect or the Improvement requirement of prior art, the invention provides a kind of low frequency three-dimensional isolation automotive seat based on the design of magnetic force Negative stiffness spring, its object is to overcome general-utility car seat can not the low-frequency vibration of level of isolation direction, vertical direction vibration can only be isolated, be not suitable for the problem of multi-dimensional vibration environment, whole system structure is simple simultaneously, does not need the vibration isolating effect that the parts of accurate design and processing just can arrive.
To achieve these goals, the technological scheme that the present invention takes, by reference to the accompanying drawings:
Based on a low frequency three-dimensional isolation automotive seat for magnetic force Negative stiffness spring design, be made up of vertical vibration isolation part and horizontal vibration isolation part, horizontal vibration isolation partial fixing is connected to above vertical vibration isolation part; Described vertical vibration isolation part comprises scissors suspension and zero stiffness magnetic damper 4, described scissors suspension comprises scissors suspension top 1 and scissors suspension bottom 2, scissors suspension comprises between scissors suspension top 1 and scissors suspension bottom 2 and is connected with articulated linkage mechanism, scissors suspension bottom 2 is fixed with flap 3, zero stiffness magnetic damper 4 two ends respectively with scissors suspension top 1 and flap 3 hinged.
Described a kind of low frequency three-dimensional isolation automotive seat based on the design of magnetic force Negative stiffness spring, wherein, articulated linkage mechanism comprises two groups of cross link be arranged in parallel, two long strand drilling bolts 12 and two horizontal bearing pins 10, two long strand drilling bolts 12 are fixedly mounted on scissors suspension top 1 and scissors suspension bottom 2 respectively, two horizontal bearing pins 10 are slidably connected at scissors suspension top 1 and scissors suspension bottom 2 respectively, often organize cross link to intersect pin joint by two connecting rods 8 and form, every root connecting rod 8 all one end is hinged with the long drilling bolt 12 that twists, in addition one end and transverse horizontal bearing pin 10 hinged.
Described a kind of low frequency three-dimensional isolation automotive seat based on the design of magnetic force Negative stiffness spring, wherein, zero stiffness magnetic damper 4 comprises work cylinder barrel, outer permanent magnet 17, piston rod 13, pneumatic spring 20, floating piston 19, piston rod 13 inserts makes cylinder barrel and the cylinder barrel 14 that can relatively work slides axially altogether, piston rod 13 bottom is fixed with interior permanent magnet 22, work cylinder barrel comprises the top work cylinder barrel 14 that is fixedly connected with and bottom and to work cylinder barrel 15, outer permanent magnet 17 is equipped with by permanent magnet fixed base 23 in the middle of top and the bottom work cylinder barrel, permanent magnet fixed base 23 is provided with rebound valve 24 and compression valve 16, pneumatic spring 20 is arranged on the bottom of lower work cylinder barrel 15, floating piston 19 is arranged on above pneumatic spring 20, floating piston 19 is flexibly connected with lower work cylinder barrel 15 inner wall sealing, damp liquid 21 is filled above floating piston 19.Vibration isolation principle on vertical direction is: zero stiffness electromagnetic damper and scissors suspension concur the low-frequency vibration of vibration isolation vertical direction.When automobile is by convex road surface or when walking out recessed road surface, work cylinder barrel moves relative on piston rod, pneumatic spring compresses, motion stops is moved, the elastic force of pneumatic spring increases, but due to electromagnet Negative stiffness spring magnetic force, the stressed of piston rod is made to be still state of equilibrium, therefore piston rod position is constant relative to scissors suspension top, corresponding driver displacement of vertical direction in cockpit is close to zero, otherwise when automobile is by recessed road surface or when walking out convex road surface, pneumatic spring and negative stiffness magnetic spring contrary to the active force of piston rod, piston rod is made still to be in state of equilibrium, thus decay vertical direction vibrates.
Described a kind of low frequency three-dimensional isolation automotive seat based on the design of magnetic force Negative stiffness spring, wherein, horizontal vibration isolation part comprises upper board 25, rubber damping spring seat 26, main magnet group 27, external magnet group 28, seat fixing frame 29, upper board 25 is fixed on above described scissors suspension, rubber damping spring seat 26 is fixed on upper board 25, seat fixing frame 29 bolt is connected on rubber damping spring seat 26, boss is provided with and boss peripheral bond main magnet group 27 in upper board 25 center upper portion, seat fixing frame 29 bottom is provided with boss and bonding with external magnet group 28 inside boss, main magnet group 27 is positioned at the centre of external magnet group 28.Substantially horizontal vibration isolation principle: when seat is by substantially horizontal vibration, seat basin connecting plate horizontal vibration, rubber shock-absorbing spring horizontal is vibrated, magnet Relative Vibration on base plate simultaneously, rubber spring and the active force of magnetic force Negative stiffness spring to upper board make upper board keep less vibration displacement, thus level of isolation direction vibrates.
By above technological scheme compared with prior art, vibration isolation automotive seat of the present invention is divided into vertical vibration isolation part and horizontal vibration isolation part, is fixedly connected with between two-part.In the vertical direction adopts the structure of electromagnetic force Negative stiffness spring and the positive rigid spring parallel connection of gas, can by regulating the size of electromagnetic force, regulate the rigidity size of the electromagnetic force Negative stiffness spring on vertical direction, adopt the effect that magnetic spring provides negative stiffness and rubber spring to provide the form of positive rigidity to be up to the standard direction vibration isolation in the horizontal direction.
In general, the present invention is Nonlinear Vibration Isolation System, adds the vibration isolation dimension of existing automotive seat, has vertically, the three-dimensional vibration isolating effect of level, improves driver's overall comfort.The present invention is on the basis of existing automotive seat, improve the vibration isolating effect on original vertical direction, and increase the arrangement space of other parts of automobile, add horizontal isolation mounting, decrease horizontal vibration to affect driver, the advantages such as it is simple that the parts newly increased have structure, easy to use.
Accompanying drawing illustrates:
Fig. 1 is vibration isolation automotive seat three-dimension integrally structural representation of the present invention.
Fig. 2 is the present invention's vertical vibration isolation partial 3-D structural representation.
Fig. 3 is the graphics of the present invention's vertical vibration isolation part zero stiffness magnetic damper.
Fig. 4 is the internal structure sectional drawing of the present invention's vertical vibration isolation part zero stiffness magnetic damper.
Fig. 5 is partial enlargement free-body diagram under the present invention's vertical vibration isolation part zero stiffness magnetic damper static balancing state.
Fig. 6 is partial enlargement free-body diagram under the present invention's vertical vibration isolation part zero stiffness magnetic damper vibrational state.
Fig. 7 is that the horizontal vibration isolation part first of the present invention implements schematic three dimensional views.
Fig. 8 is that the present invention's horizontal vibration isolation part first implements three-dimensional partial sectional view.
Fig. 9 is that the horizontal vibration isolation part first of the present invention implements rubber damping spring seat schematic three dimensional views.
Figure 10 is that the horizontal vibration isolation part first of the present invention implements upper board schematic three dimensional views.
Figure 11 is that the horizontal vibration isolation part first of the present invention implements seat fixing frame schematic three dimensional views.
Figure 12 is the present invention's horizontal vibration isolation part first embodiment section vibrational state lower stress figure.
Figure 13 is the present invention's horizontal vibration isolation part second embodiment schematic three dimensional views.
Figure 14 is the three-dimensional partial sectional view of the present invention's horizontal vibration isolation part second embodiment.
Embodiment
Design of vibration isolator thought provided by the invention is: utilize the magnetic element with negative stiffness in parallel with the elastic element with positive rigidity, thus reduce substantially horizontal and vertical vibration.
Below in conjunction with accompanying drawing, the specific embodiment of the present invention is described further.It should be noted that at this, the explanation for these mode of executions understands the present invention for helping, but does not form limitation of the invention.In addition, if below in described each mode of execution of the present invention involved technical characteristics do not form conflict each other and just can mutually combine.
As shown in Figure 1, based on the low frequency three-dimensional isolation automotive seat of magnetic force Negative stiffness spring design, be made up of vertical vibration isolation part and horizontal vibration isolation part, vertical vibration isolation part and horizontal vibration isolation part serve vertical direction and horizontal plane all directions vibration isolation effect respectively, be bolted between two-part or directly weld, in this example, vertical direction vibration isolation part under, substantially horizontal vibration isolation part is upper.
Be illustrated in figure 2 vertical vibration isolation part, vertical vibration isolation part is made up of scissors suspension, flap 3, zero stiffness magnetic damper 4, first damper bearing pin 6, second damper bearing pin 7.Scissors suspension frame structure: scissors suspension lower base 2 and vehicle body are connected, flap 3 is welded on scissors suspension bottom 2, articulated linkage mechanism is connected with between scissors suspension bottom 2 and scissors suspension top 1, articulated linkage mechanism comprises two groups of cross link be arranged in parallel, often organize cross link to be formed by pin 11 interconnection by the middle of two connecting rods 8, two horizontal bearing pins 10 are slidably connected respectively by roller ball bearing and scissors suspension top 1 and scissors suspension bottom 2, two long strand drilling bolts 12 are connected by nut with scissors suspension top 1 and scissors suspension bottom 2 respectively, every root connecting rod 8 all one end is hinged with the long drilling bolt 12 that twists, in addition one end and transverse horizontal bearing pin 10 hinged.In this example based on scissors suspension, zero stiffness magnetic damper 4 top is connected with upper ear piece 9 by the first damper bearing pin 6, zero stiffness magnetic damper 4 bottom is connected with lower ear piece 5 by the second damper bearing pin 7, upper ear piece 9 is connected by bolt and scissors suspension 1 top, and lower ear piece 5 is fixedly connected with flap 3 by bolt.
As the graphics that Fig. 3 is zero stiffness magnetic damper.Zero stiffness magnetic damper is made up of parts such as the cylinder barrel 14 that works, outer permanent magnet 17, piston rod 13, pneumatic springs 20.Work cylinder barrel 14 is divided into work cylinder barrel 14 and bottom, top to work cylinder barrel 15 two-part, centre connects with bolt, piston rod 13 inserts makes cylinder barrel 14 altogether, between top work cylinder barrel 14 and piston rod 13, sliding bearing is housed, and piston rod 13 cylinder barrel 14 that can relatively work is slid axially.For further illustrating its internal structure, Fig. 4 is the internal structure sectional drawing of zero stiffness magnetic damper: as shown in Figure 4, the bottom of top work cylinder barrel 14 is jagged, axially locating is carried out with bottom clutch release slave cylinder 15, the upper boss of bottom work cylinder barrel 15 is stuck in the breach of work cylinder barrel 14 bottom, top, and add packing ring in centre, play sealing and positioning action, outer permanent magnet 17 (upwards, S is extremely downward in N pole) is equipped with by permanent magnet fixed base 23 in the middle of upper and lower two work cylinder barrels; The foot of lower work cylinder barrel 15 is pneumatic spring 20.Be floating piston 19 above pneumatic spring 20, floating piston 19 can slide along lower work cylinder barrel 15 inwall, seals, fill damp liquid 21 above floating piston 19 with Rubber O-ring 18, and floating piston 19 completely cuts off pneumatic spring 20 and damp liquid 21.Piston rod 13 bottom is provided with ladder, is used for locating interior permanent magnet 22, and axial restraint is carried out by nut and packing ring in permanent magnet 22 bottom, and permanent magnet fixed base 23 is provided with rebound valve 24 and compression valve 16.
The vibration isolation principle of vertical direction vibration isolation part:
Zero stiffness magnetic damper 4 and scissors suspension concur the low-frequency vibration of vibration isolation vertical direction.As shown in Figure 5, when resting, pneumatic spring 20 compresses, and rebound valve 24 and compression valve 16 are in closed condition, and the elastic force F1 of pneumatic spring 20 is passed to permanent magnet fixed base 23 by damp liquid 21, and the extruding force F2 be subject to piston balances each other.Now, the central position of interior permanent magnet 22 and outer permanent magnet 17 is just in time corresponding, and between two magnet, magnetic force makes a concerted effort to be zero, and piston rod 13 is in static balancing state.When automobile is by convex road surface or when going out recessed road surface, as shown in Figure 6, work cylinder barrel 15 moves relative on piston rod 13, pneumatic spring 20 compresses, and floating piston 19 moves down, and the elastic force of pneumatic spring 20 increases to f, and now rebound valve 24 is opened, below damp liquid 21 is flowed in the cavity of top by rebound valve 24, produces damping force F 4 upwards, makes system produce forward rigidity
due to work cylinder barrel moving, cause outer permanent magnet 16 moves, produce downward magnetic force F3, thus make system produce negative sense rigidity
the now global stiffness K of system
perpendicular=K
just+ K
negativelevel off to zero.Therefore, piston rod position is constant relative to scissors suspension top 1, there is no vibration passing on piston rod 13, thus isolation is vibrated from scissors suspension bottom 2 vertical direction, otherwise when automobile is by recessed road surface or when walking out convex road surface, the positive stiffness K that the active force of pneumatic spring 20 and damp liquid 21 pairs of piston rods 13 makes system produce
just, interior permanent magnet 22 and outer permanent magnet 17 mutually magnetic force make system produce negative stiffness K
negative, the now global stiffness K of system
perpendicular=K
just+ K
negativelevel off to zero, make the vertical direction natural frequency of seat
level off to zero, and then the outer bound pair seat system vertical direction of isolation vibrates.
Described horizontal vibration isolation part is arranged in vertical vibration isolation part top or bottom, and this example is described to be in top.Fig. 7 is horizontal plane vibration isolation part first embodiment schematic diagram, and Fig. 8 is Fig. 7 part partial schematic sectional view, and horizontal vibration isolation part is made up of parts such as upper board 25, rubber damping spring seat 26, main magnet group 27, external magnet group 28, seat fixing frames 29.Upper board 25 welds or bolt is fixed on above scissors suspension, and rubber damping spring seat 26 (Fig. 9 is its three-dimensional structure) is connected with upper board 25 by bolt, and rubber damping spring seat 26 top and seat fixing frame 29 are bolted; Be provided with boss in upper board 25 center upper portion, boss peripheral bond main magnet group 27, its assembly relation as shown in Figure 10; Be provided with boss in seat fixing frame 29 bottom, seat fixing frame 29 lower boss is coaxially positioned at outside upper board 25 upper boss, and bonding with external magnet group 28 inside seat fixing frame 29 lower boss, and its assembly relation as shown in figure 11; During assembling, main magnet group 27 is in the centre of external magnet group 28, and main magnet group 27 is mutually corresponding with external magnet group 28.
Substantially horizontal vibration isolation principle:
Main magnet periphery is N pole, and inside is S pole, and the peripheral magnet magnetic pole corresponding with main magnet is S pole, and opposite direction is N pole.When vehicle stationary time, main magnet group 27 is in external magnet group 28 neutral position.As shown in figure 12, when vehicle level vibrates, vehicle seat suspension occurred level direction is caused to vibrate, without loss of generality, when vibrating left in the drawings for upper board 25, because main magnet group 27 and upper board 25 are connected, main magnet group 27 is moved to the left relative to peripheral magnet 28, be right F ' to the direction of the power of peripheral magnet 28, produce negative stiffness
and upper board 25 is moved to the left, cause rubber damping spring seat 26 to be moved to the left, to seat fixing frame 29 horizontal pull F, direction is left, produces positive stiffness K
just, because positive Negative stiffness spring is in parallel, then global stiffness K
flat=K
just+ K
negativelevel off to zero, otherwise when upper board is to other direction horizontal vibration, due to the interaction of rubber spring and magnetic force Negative stiffness spring, make seat horizontal directional stiffness K
flat=K
just+ K
negativelevel off to zero, natural frequency on seat horizontal direction
level off to zero, thus the vibration in level of isolation direction.
Figure 13 is horizontal vibration isolation part second embodiment 3-D view.Figure 14 is horizontal vibration isolation part second example partial sectional view 3-D view.This isolation mounting is made up of parts such as upper board 25, rubber damping spring seat 26, main magnet group 27, external magnet group 28, seat fixing frames 29.Upper board 25 welds or bolt is fixed on above scissors suspension, and rubber damping spring seat 26 is connected with upper board 25 by bolt, and rubber damping spring seat 26 top and seat fixing frame 29 are bolted; Hexagon boss is provided with in upper board 23 center upper portion, it is peripheral that main magnet group 27 is bonded in Hexagon boss, boss is provided with in seat fixing frame 29 bottom, seat fixing frame 29 lower boss is positioned at outside upper board 25 upper boss, external magnet group 28 is bonded in inside seat fixing frame 29 lower boss, main magnet group 27 is in the centre of external magnet group 28, and main magnet group 27 is mutually corresponding with external magnet group 28 plane.Its working principle is identical with example one.
The above is preferred embodiment of the present invention, but the present invention should not be confined to the content disclosed in this embodiment and accompanying drawing.The equivalence completed under not departing from spirit disclosed in this invention so every or amendment, all fall into the scope of protection of the invention.
Claims (4)
1., based on a low frequency three-dimensional isolation automotive seat for magnetic force Negative stiffness spring design, it is characterized in that, be made up of vertical vibration isolation part and horizontal vibration isolation part, horizontal vibration isolation partial fixing is connected to above vertical vibration isolation part; Described vertical vibration isolation part comprises scissors suspension and zero stiffness magnetic damper (4), described scissors suspension comprises scissors suspension top (1) and scissors suspension bottom (2), scissors suspension comprises between scissors suspension top (1) and scissors suspension bottom (2) and is connected with articulated linkage mechanism, scissors suspension bottom (2) is fixed with flap (3), zero stiffness magnetic damper (4) two ends respectively with scissors suspension top (1) and flap (3) hinged.
2. as claimed in claim 1 a kind of based on magnetic force Negative stiffness spring design low frequency three-dimensional isolation automotive seat, it is characterized in that, described articulated linkage mechanism comprises two groups of cross link be arranged in parallel, two long strand drilling bolts (12) and two horizontal bearing pins (10), two long strand drilling bolts (12) are fixedly mounted on scissors suspension top (1) and scissors suspension bottom (2) respectively, two horizontal bearing pins (10) are slidably connected at scissors suspension top (1) and scissors suspension bottom (2) respectively, often organize cross link to be made up of two connecting rods (8) intersection pin joints, every root connecting rod (8) all one end is hinged with the long drilling bolt (12) that twists, in addition one end and transverse horizontal bearing pin (10) hinged.
3. as claimed in claim 1 a kind of based on magnetic force Negative stiffness spring design low frequency three-dimensional isolation automotive seat, it is characterized in that, described zero stiffness magnetic damper (4) comprises work cylinder barrel, outer permanent magnet (17), piston rod (13), pneumatic spring (20), floating piston (19), piston rod (13) inserts work cylinder barrel (14) and the cylinder barrel that can relatively work slides axially, piston rod (13) bottom is fixed with interior permanent magnet (22), work cylinder barrel (14) comprises top work cylinder barrel (14) be fixedly connected with and to work cylinder barrel (15) with bottom, outer permanent magnet (17) is equipped with by permanent magnet fixed base (23) in the middle of top and the bottom work cylinder barrel, permanent magnet fixed base (23) is provided with rebound valve (24) and compression valve (16), pneumatic spring (20) is arranged on the bottom of lower work cylinder barrel (15), floating piston (19) is arranged on pneumatic spring (20) top, floating piston (19) is flexibly connected with lower work cylinder barrel (15) inner wall sealing, damp liquid (21) is filled in floating piston (19) top.
4. as claimed in claim 1 a kind of based on magnetic force Negative stiffness spring design low frequency three-dimensional isolation automotive seat, it is characterized in that, described horizontal vibration isolation part comprises upper board (25), rubber damping spring seat (26), main magnet group (27), external magnet group (28), seat fixing frame (29), upper board (25) is fixed on above described scissors suspension, rubber damping spring seat (26) is fixed on upper board (25), seat fixing frame (29) bolt is connected on rubber damping spring seat (26), boss is provided with and boss peripheral bond main magnet group (27) in upper board (25) center upper portion, seat fixing frame (29) bottom is provided with boss and bonding with external magnet group (28) inside boss, main magnet group (27) is positioned at the centre of external magnet group (28).
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| Application Number | Priority Date | Filing Date | Title |
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| CN201510989738.XA CN105546026B (en) | 2015-12-24 | 2015-12-24 | The low frequency three-dimensional isolation quarry tipper seat designed based on magnetic force Negative stiffness spring |
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| CN201510989738.XA CN105546026B (en) | 2015-12-24 | 2015-12-24 | The low frequency three-dimensional isolation quarry tipper seat designed based on magnetic force Negative stiffness spring |
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| CN105546026A true CN105546026A (en) | 2016-05-04 |
| CN105546026B CN105546026B (en) | 2017-10-10 |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN106960096A (en) * | 2017-03-24 | 2017-07-18 | 哈尔滨工业大学 | Three-dimensional negative stiffness honeycomb and preparation method thereof |
| CN109532589A (en) * | 2018-12-21 | 2019-03-29 | 安徽工程大学 | Double-layer vibration isolating seat |
| CN109780124A (en) * | 2019-01-18 | 2019-05-21 | 华东交通大学 | A kind of negative stiffness vibration absorber of parallel connection Frequency Adjustable |
| CN109941167A (en) * | 2019-04-27 | 2019-06-28 | 吉林大学 | Off highway vehicle seat horizontal vibration isolation suspension |
| CN110454544A (en) * | 2019-08-12 | 2019-11-15 | 西北工业大学 | A kind of non-linear rigidity vibration-isolating platform for optoelectronic device |
| CN110645314A (en) * | 2019-10-17 | 2020-01-03 | 贵州詹阳动力重工有限公司 | Quasi-zero stiffness vibration isolator with low-frequency broadband characteristic |
| CN110857718A (en) * | 2018-08-23 | 2020-03-03 | 张家铭 | Geometric non-linear vibration isolation system |
| CN112172632A (en) * | 2020-09-25 | 2021-01-05 | 中国直升机设计研究所 | Variable-pressure active liquid vibration isolation seat system |
| CN113954710A (en) * | 2021-12-09 | 2022-01-21 | 北京环境特性研究所 | Nonlinear seat suspension |
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| CN106960096A (en) * | 2017-03-24 | 2017-07-18 | 哈尔滨工业大学 | Three-dimensional negative stiffness honeycomb and preparation method thereof |
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| CN110454544A (en) * | 2019-08-12 | 2019-11-15 | 西北工业大学 | A kind of non-linear rigidity vibration-isolating platform for optoelectronic device |
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