CN101994776B - Two-free endpoint dynamic vibration absorber - Google Patents

Two-free endpoint dynamic vibration absorber Download PDF

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Publication number
CN101994776B
CN101994776B CN 201010281992 CN201010281992A CN101994776B CN 101994776 B CN101994776 B CN 101994776B CN 201010281992 CN201010281992 CN 201010281992 CN 201010281992 A CN201010281992 A CN 201010281992A CN 101994776 B CN101994776 B CN 101994776B
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damper
spring
free
accumulator
vibration absorber
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CN101994776A (en
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陈龙
张孝良
聂佳梅
江浩斌
汪若尘
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Jiangsu University
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Jiangsu University
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Abstract

The invention discloses a two-free endpoint dynamic vibration absorber, relating to the technical field of dynamic vibration absorber. The two-free endpoint dynamic vibration absorber comprises a spring (1), a damper (2) and an inertial mass energy accumulator (8); wherein the spring (1) is connected with the damper (2) in parallel and then is connected with the inertial mass energy accumulator (8) in series; the spring (1) is a helical compression one, and the damper (2) is a drum-type hydraulic one. The invention can be applied to the occasion that an endpoint can not be taken as a reference point and grounded and has wider application range compared with the traditional dynamic vibration absorber; the vibration absorber is provided with two free endpoints and can be placed horizontally, vertically and obliquely, vibration of master vibrator at any direction can be absorbed, thus being convenient to mount the vibration absorber; the inertial mass energy accumulator has the function of amplifying mass property, the weight thereof is far lighter than a mass element, thus greatly reducing the weight of large-scale dynamic vibration absorber.

Description

Two free end point power bump levellers
Technical field
The present invention relates to the dynamic vibration absorber technical field, refer in particular to the dynamic vibration absorber with two free end points.
Background technique
Dynamic vibration absorber claims tuned mass damper (Tuned mass damper again, TMD), its basic principle is: by adding a substructure (being bump leveller) in target vibration system (namely main shaking is), the structural type of suitable chooser structure, kinetic parameter and the coupled relation that shakes and be with the master, change the main vibrational state that shakes and be, thereby reduce the main forced vibration response of shaking and being in the frequency range of expection.Because it is simple in structure, easy to implement, effectively blanketing frequency changes the small device vibration, on the various machinery of all trades and professions such as therefore be widely used in communications and transportation, industrial machinery, build a bridge, has become and has implemented one of the most frequently used important means of vibration control.In recent years, though the research of active/semi-active type dynamic vibration absorber and application make significant progress, the passive type bump leveller is still the main flow that engineering is used, and correlative study has also obtained many new developments.
As shown in Figure 1, traditional power bump leveller 5 comprises spring 1, damper 2 and quality 3, quality 3 by spring 1 and damper 2 be suspended to main shake be under.Because traditional power bump leveller 5 has adopted mass elements, causes its application area to be restricted.In traditional power bump leveller 5, after spring 1 and damper 2 parallel connections two public end points are arranged, one of them end points links to each other with mass elements 3, obviously, 5 of traditional power bump levellers have a free end points, and therefore the necessary conduct of another end points is requiring end points can not put the occasion of ground connection as reference with reference to some ground connection, traditional power bump leveller 5 has just shown certain narrow limitation, and its application area is restricted.
For example, multilayer vibration insulation structure as shown in Figure 2 comprise main shake be 4, traditional power bump leveller 5, carrier 6 and inertial reference frame 7 (the earth), if the master is shaken is 4 to be embodied as explosive motor with being without loss of generality, carrier 6 is embodied as vehicle body, then traditional power bump leveller 5 is equivalent to be placed between motor and the inertial reference frame 7, as shown in Figure 3.Obviously, in any case arrange, traditional power bump leveller 5 must have an end to connect inertial reference frame 7, if require bump leveller to place between motor and the vehicle body, so traditional bump leveller 5 will be no longer suitable.
From the viewpoint of power stream, be more readily understood the narrow limitation of traditional power bump leveller.For the traditional power bump leveller, power stream is flowed through behind the bump leveller, finally and forever can only flow to inertial reference frame 7 namely greatly, and can not flow to its place.For last example, even the traditional power bump leveller is placed between motor and the vehicle body, power stream also can only flow to the earth through bump leveller from motor, and can not flow to vehicle body, and any power of requirement stream all is impossible realize from motor through the attempt that the traditional power bump leveller flows to vehicle body.Therefore seek a kind of power stream and needn't flow to the earth, dynamic vibration absorber that namely needn't ground connection is significant.
The traditional power bump leveller is arranging to also have its inconvenience.Though the traditional power bump leveller is arranged when absorbing vertical vibration than be easier to, arrange inconvenience is then arranged when absorbing the vibration of other direction more; In addition, the mass elements required as if dynamic vibration absorber is heavier, then can cause bump leveller integral body overweight.
US Patent No. 989958 discloses a kind of original dynamic vibration absorber, US Patent No. 6681908 discloses the adjustable dynamic vibration absorber of a kind of spring, US Patent No. 5816373 discloses a kind of pneumatic power bump leveller, yet these bump levellers adopt mass elements as one of its assembly bar none, also certainly exist above-mentioned inconvenience and narrow limitation, therefore the dynamic vibration absorber of seeking a kind of applied range and arranging flexibly and easily has realistic meaning, seems particularly urgent.
Summary of the invention
Technical problem to be solved by this invention is: allow dynamic vibration absorber have two free end points, make bump leveller can be applied to require end points not enlarge the application area of dynamic vibration absorber as the occasion with reference to some ground connection; After dynamic vibration absorber had two end points, an end was to link to each other with main shaking, and the other end can free alternative point of contact, and bump leveller can horizontal, perpendicularly be put with tilting, makes things convenient for installation and the layout of bump leveller, and it is vibration that the master who absorbs any direction shakes; Utilize the inertial mass accumulator to be lighter than the characteristics of mass elements far away, reduce the weight of large-sized power bump leveller.
The present invention solves this technical problem the technological scheme that adopts: earlier spring and damper are connected in parallel, doublet and the inertial mass accumulator with them is connected in series again.Spring is spiral compression spring, and damper is the cylinder type hydraulic damper.
According to different inertial mass accumulator ways of realization, the present invention has two kinds of concrete technological schemes.
Scheme one
Two free end point power bump levellers comprise spring, damper and rack-type inertial mass accumulator.Spring housing is outside the urceolus of damper, and spring is connected with damper is coaxial, and an end of spring is fixedlyed connected with the piston rod of damper, and the other end of spring is fixedlyed connected with the urceolus of damper; Coaxial the fixedlying connected of tooth bar of the piston rod of damper and rack-type inertial mass accumulator.
Rack-type inertial mass accumulator comprises casing, flywheel A, gear shaft A, gearwheel, gear shaft B and tooth bar, its middle rack places in the dovetail groove on the casing, B is meshed with gear shaft, gearwheel links with gear shaft B is coaxial, A is meshed with gear shaft, flywheel A then links with gear shaft A is coaxial, and gear shaft A and gear shaft B all are supported on the casing by pair of bearings.
Scheme two
Two free end point power bump levellers comprise spring, damper and twisting inertia quality accumulator.Spring housing is outside the urceolus of damper, and spring is connected with damper is coaxial, and an end of spring is fixedlyed connected with the piston rod of damper, and the other end of spring is fixedlyed connected with the urceolus of damper; The fork of the piston rod of damper and twisting inertia quality accumulator is hinged, and when the equilibrium position, the piston rod of damper is vertical mutually with fork.
Twisting inertia quality accumulator comprises fork, pedestal, cycloidal ball retarder and flywheel B.
The cycloidal ball retarder comprises input shaft, cycloidal ball driving mechanism, output shaft, housing and pre-load nut.
Flywheel B is connected with the conical surface interference that the optional key of making even of the Placement of cycloidal ball input shaft of speed reducer, rectangular spline, involute splines, screw thread or nut compress.
Fork is long strip, and an end has the hole of band keyway, is fixedly connected with the output shaft of cycloidal ball retarder, and it is hinged that the other end has the piston rod of pan and damper.
Pedestal be one be bent into 90 the degree the rectangular steel plates, half steel plate that area is big is provided with big hole, be evenly equipped with 6 small sircle holes around the big hole, the circle at place, 6 small sircle hole centers of circle is concentric with big hole, be evenly equipped with two rows totally 4 through holes on little half steel plate of area, and big hole central shaft to the distance of bending part bottom surface equals the hole of band keyway on the fork and the distance between the heart of pan hole.
Input shaft is contained in the bearing A, and passes through bearing C frame on output shaft, its eccentric position bearing set B.Different according to input shaft and flywheel Placement, the spindle nose that input shaft stretches out housing one end is circular or terminal screwed taper, circular spindle nose is provided with flat key groove, rectangle external splines groove, involute outer spline groove or the outside thread of symmetry.
The cycloidal ball driving mechanism comprises bearing A, spider, bearing B, steel ball A, planetary plate, steel ball B, bearing C, bearings D, bearing E.The spider that is connected with housing is contained on the bearing A, and it is z that its left side is provided with wave number 1The epicycloid enclosed slot; Planetary plate is contained on the bearing B, and it is z that its right side is provided with wave number 2The hypocycloid enclosed slot, it is z that the left side is provided with wave number 3The hypocycloid enclosed slot; Be bearing in the output shaft on the housing by bearings D, bearing E, its right-hand member is dish type, and it is z that dish face is provided with wave number 4The epicycloid enclosed slot; At enclosed slot z 1, z 2Steel ball A is housed, wherein z in the staggered zone 2-z 1=2, the steel ball number is (z 1+ z 2)/2; At enclosed slot z 3, z 4Steel ball B is housed, wherein z in the staggered zone 3-z 4=2, the steel ball number is (z 3+ z 3)/2; Enclosed slot z 1, z 2Form engagement pair, enclosed slot z with steel ball A 3, z 4Form another engagement pair with steel ball B.
Output shaft is discoid at an end of enclosure interior, and the spindle nose that stretches out housing one end is cylindrical, and spindle nose is provided with the flat key groove, is fixedly connected by key and fork.
Housing is thin-walled revolution workpiece, an end that supports output shaft is the conical thin-wall solid of rotation, an end that supports input shaft is circular thin-walled revolution workpiece, and the shell wall that conical thin-wall solid of rotation and circular thin-walled revolution workpiece have a common boundary is provided with the uniform tapped blind hole of axle centered by rotary middle spindle, and quantity is 6.6 small sircle holes on the pedestal are corresponding with 6 tapped holes on the housing, connect by bolt is corresponding.
The present invention makes dynamic vibration absorber have two end points freely, the casing of the urceolus of damper and rack-type inertial mass accumulator is two free end points of dynamic vibration absorber in the scheme one, the pedestal of the urceolus of damper and twisting inertia quality accumulator is two end points of dynamic vibration absorber in the scheme two, and dynamic vibration absorber has and possessed following advantage behind two free end points:
1, two free end point power bump levellers can be applied to require end points can not put the occasion of ground connection as reference, than the applied range of traditional power bump leveller.
2, after dynamic vibration absorber has two end points, one end can be to link to each other with main shaking, and the other end can free alternative point of contact, makes bump leveller horizontal, perpendicularly to put with tilting, it is vibration that the master of absorption any direction shakes, and greatly facilitates installation and the layout of bump leveller.
3, because the inertial mass accumulator also has the effect of amplifying qualitative attribute, and its weight is lighter than mass elements far away, therefore can reduce the weight of large-sized power bump leveller greatly.
Description of drawings
Fig. 1 is traditional power bump leveller structural representation;
Fig. 2 arranges schematic representation for the traditional power bump leveller;
Fig. 3 is that traditional power bump leveller and inertial reference frame (the earth) concern schematic representation;
Fig. 4 is two free end point power bump leveller structural representations;
Fig. 5 is the two free end point power bump leveller structural representations of having used rack-type inertial mass accumulator;
Fig. 6 is rack-type inertial mass accumulator structure schematic representation;
Fig. 7 is the two free end point power bump leveller structural representations of having used twisting inertia quality accumulator;
Fig. 8 is twisting inertia quality accumulator structure schematic representation;
Fig. 9 is cycloidal ball reducer structure schematic representation;
Figure 10 is the pedestal plan view;
Figure 11 is the pedestal right elevation;
Figure 12 is the perpendicular scheme of installations of putting of two free end point power bump levellers;
Figure 13 is the horizontal scheme of installations of two free end point power bump levellers;
Figure 14 is the tilting scheme of installations of two free end point power bump levellers;
Figure 15 is combined type two free end point power bump leveller structural representations.
Figures, 1 - spring,, 2 - damper,, 3 - Quality,, 4 - main vibration system,, 5 - traditional dynamic vibration absorber,, 6 - carrier,, 7 - Inertial Reference System,, 8 - inertial mass accumulator,, 9 - rack inertial mass accumulator,, 10 - cabinet,, 11 - flywheel A,, 12 - gear Shaft A,, 13 - large gear,, 14 - gear Shaft B,, 15 - rack,, 16 - reversing inertial mass accumulator,, 17 - pendulum,, 18 - dock,, 19 - cycloid ball reducer,, 20 - flywheel B,, 21 - input shaft,, 22 - bearing A,, 23 - center plate,, 24 - bearing B,, 25 - ball A,, 26 - planet disc 27 - ball B,, 28 - output shaft,, 29 - housing,, 30 - bearings C,, 31 - bearing D,, 32 - bearing E,, 33 - preload nut,, 34 - two free endpoints dynamic vibration absorber
Embodiment
The invention will be further described below in conjunction with drawings and Examples.
The present invention includes spring 1, damper 2 and inertial mass accumulator 8.Spring and damper are for being connected in parallel, and their doublet and inertial mass accumulator are for being connected in series.Spring 1 is spiral compression spring, and damper 2 is the cylinder type hydraulic damper.
According to two kinds of different inertial mass accumulator 8 ways of realization, divide two embodiments that the present invention is illustrated below.
Embodiment one
Two free end point power bump levellers 34 comprise spring 1, damper 2 and rack-type inertial mass accumulator 9.Spring 1 is enclosed within outside the urceolus of damper 2, spring 1 and 2 coaxial connections of damper, and an end of spring 1 is fixedlyed connected with the piston rod of damper 2, and the other end of spring 1 is fixedlyed connected with the urceolus of damper 2; Tooth bar 15 coaxial the fixedlying connected of the piston rod of damper 2 and rack-type inertial mass accumulator 9.
Rack-type inertial mass accumulator 9 comprises casing 10, flywheel A11, gear shaft A12, gearwheel 13, gear shaft B14 and tooth bar 15, its middle rack 15 places in the dovetail groove on the casing 10, B14 is meshed with gear shaft, gearwheel 13 links with gear shaft B14 is coaxial, A12 is meshed with gear shaft, flywheel A11 then links with gear shaft A12 is coaxial, and gear shaft A12 and gear shaft B14 all are supported on the casing 10 by pair of bearings.
Be described further below in conjunction with the specific implementation process of accompanying drawing to embodiment one.
As illustrated in Figures 5 and 6, when main shaking can stretch and compress spring 1 and damper 2 when being vibration, thereby drive tooth bar 15 with A or the motion of B direction, namely when external force puts on casing 10 and tooth bar 15 terminal with direction A or B, tooth bar 15 can produce relative displacement with respect to casing 10, driven gear axle B14, gearwheel 13 and gear shaft A12 rotation, and then drive flywheel A11 rotation.
In fact, in movement process, tooth bar 15 will be done straight line motion with respect to casing 10, and tooth bar 15 and casing 10 are exactly two end points of rack-type inertial mass accumulator 9.Its kinetic equations is f=ba, and wherein f, a and b represent to be applied to the power on the two-end-point, relative acceleration and the inertial mass coefficient of two-end-point respectively, and the inertial mass coefficient can be calculated by the radius of gear train and the rotary inertia of flywheel.If the tooth radius of gear shaft B 14 is r 1, gearwheel 13 radiuses are r 2, gear shaft A12 radius is r 3, the turning radius of flywheel A11 is γ, quality is m.Can derive following relation by Newton's second law:
b = m α 1 2 α 2 2
α in the formula 1=γ/r 3, α 2=r 2/ r 1According to following formula, the size that changes flywheel and gear train just can obtain having the rack-type inertial mass accumulator of suitable inertial mass coefficient.
By the spring rate of Regulation spring 1, the inertial mass coefficient b of the damping constant of damper 2 and rack-type inertial mass accumulator 9 can change the main vibrational state that shakes and be, thereby reduces the main forced vibration response of shaking and being in the frequency range of expection.
Embodiment two
Two free end point power bump levellers 34 comprise spring 1, damper 2 and twisting inertia quality accumulator 16.Spring 1 is enclosed within outside the urceolus of damper 2, spring 1 and 2 coaxial connections of damper, and an end of spring 1 is fixedlyed connected with the piston rod of damper 2, and the other end of spring 1 is fixedlyed connected with the urceolus of damper 2; The fork 17 of the piston rod of damper 2 and twisting inertia quality accumulator 16 is hinged, and when the equilibrium position, the piston rod of damper 2 is vertical mutually with fork 17.
Twisting inertia quality accumulator 16 comprises fork 17, pedestal 18, cycloidal ball retarder 19 and flywheel B20.
Cycloidal ball formula retarder 19 comprises input shaft 21, cycloidal ball driving mechanism, output shaft 28, housing 29 and pre-load nut 33.
Flywheel B20 is connected with the conical surface interference that the optional key of making even of the Placement of the input shaft 21 of cycloidal ball retarder 19, rectangular spline, involute splines, screw thread or nut compress.
Fork 16 is long strip, and an end has the hole of band keyway, is fixedly connected with the output shaft 28 of cycloidal ball retarder 19, and it is hinged that the other end has the piston rod of pan and damper 2.
Pedestal 18 be one be bent into 90 the degree the rectangular steel plates, half steel plate that area is big is provided with big hole, be evenly equipped with 6 small sircle holes around the big hole, the circle at place, 6 small sircle hole centers of circle is concentric with big hole, be evenly equipped with two rows totally 4 through holes on little half steel plate of area, and big hole central shaft to the distance of bending part bottom surface equals the hole of band keyway on the fork 17 and the distance between the heart of pan hole.
Input shaft 21 is contained in the bearing A22, and passes through bearing C30 frame on output shaft 28, its eccentric position bearing set B24.Different according to input shaft 21 and flywheel B20 Placement, the spindle nose that input shaft 21 stretches out housing one end is circular or terminal screwed taper, circular spindle nose is provided with flat key groove, rectangle external splines groove, involute outer spline groove or the outside thread of symmetry.
The cycloidal ball driving mechanism comprises bearing A22, spider 23, bearing B24, steel ball A25, planetary plate 26, steel ball B27, bearing C30, bearings D 31, bearing E32.The spider 23 that is connected with housing 29 is contained on the bearing A22, and it is z that its left side is provided with wave number 1The epicycloid enclosed slot; Planetary plate 26 is contained on the bearing B24, and it is z that its right side is provided with wave number 2The hypocycloid enclosed slot, it is z that the left side is provided with wave number 3The hypocycloid enclosed slot; Be bearing in output shaft 28 on the housing 29 by bearings D 31, bearing E32, its right-hand member is dish type, and it is z that dish face is provided with wave number 4The epicycloid enclosed slot; At enclosed slot z 1, z 2Steel ball A25 is housed, wherein z in the staggered zone 2-z 1=2, the steel ball number is (z 1+ z 2)/2; At enclosed slot z 3, z 4Steel ball B27 is housed, wherein z in the staggered zone 3-z 4=2, the steel ball number is (z 3+ z 3)/2; Enclosed slot z 1, z 2Form engagement pair, enclosed slot z with steel ball A25 3, z 4Form another engagement pair with steel ball B27.
The end of output shaft 28 in housing 29 inside is discoid, and the spindle nose that stretches out housing one end is cylindrical, and spindle nose is provided with the flat key groove, is fixedly connected by key and fork 17.
Housing 29 is thin-walled revolution workpiece, an end that supports output shaft 28 is the conical thin-wall solid of rotation, an end that supports input shaft 21 is circular thin-walled revolution workpiece, the shell wall that conical thin-wall solid of rotation and circular thin-walled revolution workpiece have a common boundary is provided with the uniform tapped blind hole of axle centered by rotary middle spindle, and quantity is 6.6 small sircle holes on the pedestal 18 are corresponding with 6 tapped holes on the housing 29, connect by bolt is corresponding.
Be described further below in conjunction with the specific implementation process of accompanying drawing to embodiment two
Shown in Fig. 7,8,9,10 and 11, when main shaking can stretch and compress spring 1 and damper 2 when being vibration, thereby drive fork 17 swings, namely when power f puts on fork 17 and pedestal 18 terminal, fork 17 will drive output shaft 28 and rotate, output shaft 28 then drives input shaft 21 rotations by the cycloidal ball driving mechanism, and then drives flywheel B20 rotation.Fork 17 and pedestal 18 are exactly two end points of twisting inertia quality accumulator 16.
The inertial mass coefficient of twisting inertia quality accumulator 16 Wherein m and r are respectively quality and the turning radius of flywheel B20, and n is the reduction speed ratio of cycloidal ball formula retarder 19, l be on the pedestal 18 the big hole central shaft to the distance of bending part bottom surface.
By the spring rate of Regulation spring 1, the inertial mass coefficient b of the damping constant of damper 2 and twisting inertia quality accumulator 16 can change the main vibrational state that shakes and be, thereby reduces the main forced vibration response of shaking and being in the frequency range of expection.
Below in conjunction with accompanying drawing characteristics of the present invention are further described.
Shown in Fig. 4,5 and 7, spring 1 and damper 2 doublets have two free public points, and inertial mass accumulator 8 also is the element with two free end points, thus the doublet of spring 1 and damper 2 with just also had two free end points after inertial mass accumulator 8 is connected.
Dynamic vibration absorber has two freely behind the end points, and end points can ground connection, and the power stream of the bump leveller of also namely flowing through can flow to the earth, and therefore two free end point power bump levellers 34 can be applicable to require the end points can not be as with reference to the occasion that put ground connection.As shown in figure 12, it is 4 that two free end point power bump levellers, 34 1 termination masters shake, and the other end is carried body 6, and in this case, power stream is 4 to have flowed to carrier 6 through bump leveller from main shaking during system works; Can certainly a termination master shaking is 4, the other end ground connection, and in such cases, power stream is 4 to have flowed to the earth through bump leveller from main shaking during system works, traditional power bump leveller 5 is equivalent shown in this situation and Fig. 2 and 3.This shows that two free end point power bump levellers 34 can be applied to the occasion that traditional power bump leveller 5 can not be used, than the applied range of traditional power bump leveller.
In addition, shown in Figure 12,13 and 14, after dynamic vibration absorber has two end points, one end can be 4 to link to each other with main shaking, the other end can free alternative point of contact, make that bump leveller not only can be horizontal but also can erect and put with tilting, it is vibration that the master who absorbs any direction shakes, and greatly facilitates installation and the layout of bump leveller.
Shown in Fig. 6 and 8, utilize inertial mass accumulator 8 to be lighter than the characteristics of mass elements far away, can reduce the weight of large-sized power bump leveller.In embodiment one, if get α 12=3, the inertial mass coefficient b=81m of rack-type inertial mass accumulator then, namely inertial mass coefficient b is 81 times of flywheel A11 quality.By top calculating as can be seen, even the quality of flywheel is very little, inertial mass accumulator 8 also can show the attribute of huge quality, in fact this can be understood as, when showing identical qualitative attribute, inertial mass accumulator 8 is lighter than mass elements far away, therefore uses two free end point power bump levellers 34, can reduce the weight of large-sized power bump leveller greatly.
Figure 15 is combined type two free end point power bump levellers, by arranging one group of two free end point power bump leveller 34, suitably adjust natural frequency and the damping ratio of bump leveller, absorb the main vibrational energy that shakes and be on certain or certain several frequency ranges, thereby reduce the main forced vibration response of shaking and being.

Claims (7)

1. free end point power bump leveller, it is characterized in that, comprise spring (1), damper (2) and inertial mass accumulator (8), spring (1) and damper (2) are for being connected in parallel, and the doublet of described spring (1) and damper (2) and inertial mass accumulator (8) are for being connected in series; Described spring (1) is spiral compression spring, and described damper (2) is the cylinder type hydraulic damper; Described inertial mass accumulator (8) is twisting inertia quality accumulator (16); Described twisting inertia quality accumulator (16) comprises fork (17), pedestal (18), cycloidal ball retarder (19) and flywheel B (20); Cycloidal ball formula retarder (19) comprises input shaft (21), cycloidal ball driving mechanism, output shaft (28), housing (29) and pre-load nut (33); Coaxial the fixedlying connected of input shaft (21) of described flywheel B (20) and cycloidal ball retarder (19); Described spring (1) is enclosed within outside the urceolus of damper (2), spring (1) and coaxial connection of damper (2), and an end of described spring (1) is fixedlyed connected with the piston rod of damper (2), and the other end of described spring (1) is fixedlyed connected with the urceolus of damper (2); The fork (17) of the piston rod of described damper (2) and twisting inertia quality accumulator (16) is hinged, and when the equilibrium position, the piston rod of described damper (2) is vertical mutually with fork (17).
2. two free end point power bump levellers according to claim 1, it is characterized in that described flywheel B (20) is that the conical surface interference that flat key, rectangular spline, involute splines, screw thread or nut compress is connected one kind of Placement with the Placement of the input shaft (21) of cycloidal ball retarder (19).
3. two free end point power bump levellers according to claim 1 and 2, it is characterized in that, described fork (17) is long strip, one end has the hole of band keyway, fixedly connected with the output shaft (28) of cycloidal ball retarder (19), it is hinged that the other end has the piston rod of pan and damper (2).
4. two free end point power bump levellers according to claim 1 and 2, it is characterized in that, described pedestal (18) be one be bent into 90 the degree the rectangular steel plates, half steel plate that area is big is provided with big hole, be evenly equipped with 6 small sircle holes around the described big hole, the circle at place, 6 small sircle hole centers of circle is concentric with big hole, be evenly equipped with two rows totally 4 through holes on little half steel plate of area, and big hole central shaft to the distance of bending part bottom surface equals fork (17) and goes up the hole of band keyway and the distance between the heart of pan hole.
5. two free end point power bump levellers according to claim 1 and 2, it is characterized in that, described housing (29) is thin-walled revolution workpiece, an end that supports output shaft (28) is the conical thin-wall solid of rotation, an end that supports input shaft (21) is circular thin-walled revolution workpiece, the shell wall that conical thin-wall solid of rotation and circular thin-walled revolution workpiece have a common boundary is provided with the uniform tapped blind hole of axle centered by rotary middle spindle, and quantity is 6; 6 small sircle holes on the described pedestal (18) are corresponding with 6 tapped holes on the housing (29), connect by bolt is corresponding.
6. two free end point power bump levellers according to claim 1 and 2 is characterized in that, the spindle nose that described input shaft (21) stretches out housing (29) one ends is circular or terminal screwed taper; The spindle nose of described circle is provided with flat key groove, rectangle external splines groove, involute outer spline groove or the one kind of form of outside thread of symmetry.
7. two free end point power bump levellers according to claim 1 and 2, it is characterized in that described output shaft (28) is discoid at the inner end of housing (29), the spindle nose that stretches out housing one end is cylindric, spindle nose is provided with the flat key groove, fixedlys connected with fork (17) by key.
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9407167U1 (en) * 1994-04-29 1994-07-07 Hemscheidt Fahrwerktech Gmbh Hydropneumatic suspension system with stabilization
CN101505981A (en) * 2006-06-07 2009-08-12 李海珍 Shock absorber apparatus for reducing weight and vibration of vehicle
CN101327722B (en) * 2008-06-05 2010-08-04 江苏大学 Vehicle suspension fork with inertia energy accumulator
WO2010078471A1 (en) * 2008-12-30 2010-07-08 Darco Trust Vehicle suspension system
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