CN101954847B - Through type inertial mass energy storage suspension - Google Patents
Through type inertial mass energy storage suspension Download PDFInfo
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- CN101954847B CN101954847B CN2010102813361A CN201010281336A CN101954847B CN 101954847 B CN101954847 B CN 101954847B CN 2010102813361 A CN2010102813361 A CN 2010102813361A CN 201010281336 A CN201010281336 A CN 201010281336A CN 101954847 B CN101954847 B CN 101954847B
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- swing arm
- vibration isolator
- suspension
- inertial mass
- energy storage
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Abstract
The invention discloses a through type inertial mass energy storage suspension and relates to the technical field of vehicle suspensions. The through type inertial mass energy storage suspension comprises a suspension cross beam (1), a lower-left swing arm (2), a left wheel vibration isolator (3), an upper-left swing arm (4), a vehicle body vibration isolator (5), an upper-right swing arm (8), a right wheel vibration isolator (9) and a lower-right swing arm (10). The invention not only greatly improves the comfortableness for sitting in the vehicle, but also improves the safety for driving and ensures that the integral performance of the suspension is greatly improved. The invention has the advantages of compact structure, low height, high possibility of arrangement and no need of complicated controller, control strategy and electronic element as well as energy input, low cost and high reliability.
Description
Technical field
The present invention relates to the vehicle suspension technical field, it is stressed equal to refer in particular to left and right sides suspension, and has adopted the vehicle suspension of inertial mass energy storage.
Background technology
The function of suspension mainly is to guarantee good ride comfort and stable tyre load, in addition, is suspended in when carrying out this function, also must suspension travel be controlled in the scope of permission.The passive suspension of tradition is made up of spring and damper; On the one hand; Adopt soft spring can obtain travelling comfort preferably, and on the other hand, high travelling comfort is a cost to sacrifice the suspension working space always but; Simultaneously also can produce harmful effect to driving safety, this contradiction is the difficult problem that suspension design person faces.
Chinese patent 200810123830.8 discloses a kind of vehicle suspension of using inertia energy accumulator; Comprise the doublet of forming by inertial mass energy storage and damper, and the doublet of forming by spring and damper, two doublets series connection form two grad vibration isolation formula vehicle suspensions; In theory; This suspension can effectively be alleviated the contradiction between travelling comfort and the driving safety, yet in actual application, the doublet of inertial mass energy storage and damper; Under the effect of vehicle body gravity, be easy to because of being lost efficacy by " puncture "; Therefore suspension after the inefficacy and the performance of traditional passive suspension and indistinction must solve the problem that the doublet of inertial mass energy storage and damper lost efficacy because of " puncture ", and this suspension ability is with practical value.
The disclosed a kind of vehicle suspension of German patent DE 000019958178C1; Adopt spring and mass to absorb the body vibrations energy, but adopt this form to absorb the heavier mass of body vibrations energy demand, increased the weight of suspension part greatly with the form of absorbing; Be equivalent to increase the weight of unsprung weight; Will certainly cause the increase of tire live load, worsen the driving safety of vehicle, in addition; Because this suspension has adopted the form of two-stage series connection to make suspension too high, arrange relatively difficulty.
Though active that development in recent years is got up and semi-active suspension can be alleviated the contradiction of travelling comfort and driving safety effectively, active suspension is because complex structure, poor reliability, low-response, energy consumption are high, cost is high, and large-scale application is still had any problem; Though the semi-active suspension energy consumption is low, the existence of Time Delay has limited the performance of its performance.The introducing of inertial mass energy storage; Make the improvement of passive suspension property have bigger potentiality; And the development in science and technology trend of low-carbon (LC), environmental protection, energy savings makes passive suspension come back to people's the visual field, and the research of passive suspension is come into one's own again.
Summary of the invention
Technical matters to be solved by this invention is: overcome the inertial mass energy storage under the vehicle body action of gravity easily by the technical disadvantages of " puncture "; Solve too high, the difficult technical matters of arranging of two-stage series connection suspension, a kind of vehicle suspension that can coordinate contradiction between travelling comfort and the driving safety is provided.
The present invention solves this technical problem the technical scheme that is adopted: spring A and damper A are composed in parallel the left wheel vibration isolator; Spring B, damper B and inertial mass energy storage are composed in parallel the vehicle body vibration isolator; Right wheel vibration isolator is identical with the left wheel vibration isolator, and is with swing arm under the left side and the coaxial left end that is articulated in the suspension crossbeam of upper left swing arm, same with bottom right swing arm and the coaxial right-hand member that is articulated in the suspension crossbeam of upper right swing arm; The left wheel vibration isolator is articulated between left swing arm down and the upper left swing arm; Right wheel vibration isolator is articulated between bottom right swing arm and the upper right swing arm, and the vehicle body vibration isolator is articulated between upper left swing arm and the upper right swing arm, through the mode that left and right suspension is connected; Reduce the suspension height; Suppress low frequency (vehicle body natural frequency) peak value of vehicle body normal acceleration through the vehicle body vibration isolator, suppress high frequency (natural frequency of wheel) peak value of tire live load, thereby reach the purpose of coordinating contradiction between travelling comfort and the driving safety through left and right wheel vibration isolator.
Concrete scheme of the present invention is to comprise suspension crossbeam, left side swing arm down, left wheel vibration isolator, upper left swing arm, vehicle body vibration isolator, upper right swing arm, right wheel vibration isolator and bottom right swing arm.
The suspension crossbeam is through two fixed links and body contact.
A left side is swing arm and the coaxial left end that is articulated in the suspension crossbeam of upper left swing arm down; Hinge axis swing around suspension crossbeam left end; Same bottom right swing arm and the coaxial right-hand member that is articulated in the suspension crossbeam of upper right swing arm; Around the hinge axis swing of suspension crossbeam right-hand member, upper left swing arm and upper right swing arm are vertical when balance position.
The left wheel vibration isolator is composed in parallel by spring A and damper A; Spring A is a spiral compression spring; Damper A is the cylinder type hydraulic damper, and the upper end of left wheel vibration isolator and the upper end of upper left swing arm are hinged, and the lower end of left wheel vibration isolator is articulated in the position in the swing arm outside down, a left side with left swing arm down.
Right wheel vibration isolator is identical with the left wheel vibration isolator, is composed in parallel by spring A and damper A, and the upper end of upper end and upper right swing arm is hinged, and lower end and bottom right swing arm are articulated in the position in the swing arm outside, bottom right.
The vehicle body vibration isolator is composed in parallel by spring B, damper B and inertial mass energy storage; Spring B is a spiral compression spring; Damper B is the cylinder type hydraulic damper; The inertial mass energy storage is a ball-screw inertial mass energy storage, and the two ends of vehicle body vibration isolator are hinged with the upper end of upper left swing arm and upper right swing arm respectively.
The inertial mass energy storage comprises hanger A, stroke chamber, nut, leading screw, bellows, leading screw supporting seat, flywheel, flywheel chamber and hanger B.Leading screw comprises polished rod partial sum screw thread raceway part; Flywheel is fixed in the polished rod part of leading screw, and the axis of leading screw is the S. A. of flywheel; In the leading screw supporting seat bearing is installed; Outside race cooperates with the endoporus of leading screw supporting seat; Bearing inner ring partly cooperates with the polished rod of leading screw near raceway one side, and when rotating with respect to the leading screw supporting seat with the assurance leading screw, the leading screw supporting seat is axially remaining unchanged with the position that directly makes progress to leading screw; Nut is meshed with the screw thread raceway on the leading screw; The stroke chamber is the long tubular of an end opening one end osed top, and open end is solidly set on the cylindrical of nut, and coaxial with nut to guarantee the stroke chamber, closed end links to each other with the screw portion of hanger A; The flywheel chamber also is the long tubular of an end opening one end osed top, and open end is solidly set on the cylindrical of leading screw supporting seat, and coaxial with the leading screw supporting seat to guarantee the flywheel chamber, closed end links to each other with the screw portion of hanger B; Bellows is the organ type dust boot, and an end is set in the outdoor tube of stroke, and the other end is set in the outdoor tube of flywheel; The screw portion of hanger A and hanger B, respectively with stroke chamber and flywheel chamber closed end centre hole on screw thread screw mutually, to guarantee that two hanger center-points are on the leading screw axis.
The invention has the beneficial effects as follows; Can make the low frequency peak value of vehicle body normal acceleration reduce 2～3 times; The low frequency peak value of the moving stroke of suspension reduces 30%; The high frequency peaks numerical value of tire live load reduces 20%, improves travelling comfort greatly, effective coordination contradiction between travelling comfort and the driving safety; Overcome the inertial mass energy storage under the vehicle body action of gravity easily by the technical disadvantages of " puncture "; Suspension frame structure is compact, and is highly low, is easy to arrange; Do not need complicated controller, control policy and electronic devices and components, do not need the energy input, cost is low, and reliability is high.
Description of drawings
Fig. 1 is half bassinet structure scheme drawing;
Fig. 2 is through inertial mass accumulation of energy suspension frame structure scheme drawing;
Fig. 3 is a ball-screw inertial mass energy storage outside drawing;
Fig. 4 is a ball-screw inertial mass accumulator structure exploded drawings.
Among the figure, the right wheel vibration isolator of the upper right swing arm 9-of the upper left swing arm 5-of swing arm 3-left wheel vibration isolator 4-vehicle body vibration isolator 6-vehicle body 7-fixed link 8-10-bottom right swing arm 11-spring A 12-damper A 13-spring B 14-damper B 15-inertial mass energy storage 16-hanger A 17-stroke chamber 18-nut 19-leading screw 20-bellows 21-leading screw supporting seat 22-flywheel 23-flywheel chamber 24-hanger B under the 1-suspension crossbeam 2-left side
The specific embodiment
Below in conjunction with accompanying drawing and embodiment the present invention is described further.
The present invention includes suspension crossbeam 1, left side swing arm 2 down, left wheel vibration isolator 3, upper left swing arm 4, vehicle body vibration isolator 5, upper right swing arm 8, right wheel vibration isolator 9 and bottom right swing arm 10.
Left side swing arm 2 and the upper left swing arm 4 coaxial left ends that are articulated in suspension crossbeam 1 down; Hinge axis swing around suspension crossbeam 1 left end; Same bottom right swing arm 10 and the upper right swing arm 8 coaxial right-hand members that are articulated in suspension crossbeam 1; Around the hinge axis swing of suspension crossbeam 1 right-hand member, upper left swing arm (4) and upper right swing arm (8) are vertical when balance position.
Left wheel vibration isolation 3 bodies are composed in parallel by spring A11 and damper A12; Spring A11 is a spiral compression spring; Damper A12 is the cylinder type hydraulic damper, and the upper end of the upper end of left wheel vibration isolator 3 and upper left swing arm 4 is hinged, and the lower end is articulated in the position in swing arm 2 outsides down, a left side with left swing arm 2 down.
Right wheel vibration isolator 9 is identical with left wheel vibration isolator 3, is composed in parallel by spring A11 and damper A12, and the upper end of upper end and upper right swing arm 8 is hinged, and lower end and bottom right swing arm 10 are articulated in the position in bottom right swing arm 10 outsides.
Vehicle body vibration isolator 5 is composed in parallel by spring B 13, damper B14 and inertial mass energy storage 15; Spring B 13 is a spiral compression spring; Damper B14 is the cylinder type hydraulic damper; Inertial mass energy storage 15 is a ball-screw inertial mass energy storage, and the two ends of vehicle body vibration isolator 5 are hinged with the upper end of upper left swing arm 4 and upper right swing arm 8 respectively.
Inertial mass energy storage 15 comprises hanger A16, stroke chamber 17, nut 18, leading screw 19, bellows 20, leading screw supporting seat 21, flywheel 22, flywheel chamber 23 and hanger B24.Leading screw 19 comprises polished rod partial sum screw thread raceway part; Flywheel 22 is fixed in the polished rod part of leading screw 19, and the axis of leading screw 19 is S. A.s of flywheel 22; In the leading screw supporting seat 21 bearing is installed; Outside race cooperates with the endoporus of leading screw supporting seat 21; Bearing inner ring partly cooperates with the polished rod of leading screw 19 near raceway one side; When rotating with respect to leading screw supporting seat 21 with assurance leading screw 19,21 pairs of leading screws 19 of leading screw supporting seat are axially remaining unchanged with the position that directly makes progress; Nut 18 is meshed with the screw thread raceway on the leading screw 19; Stroke chamber 17 is the long tubular of an end opening one end osed top, and open end is solidly set on the cylindrical of nut 18, and coaxial with nut 18 to guarantee stroke chamber 17, closed end links to each other with the screw portion of hanger A16; Flywheel chamber 23 also is the long tubular of an end opening one end osed top, and open end is solidly set on the cylindrical of leading screw supporting seat 21, and coaxial with leading screw supporting seat 21 to guarantee flywheel chamber 23, closed end links to each other with the screw portion of hanger B24; Bellows 20 is the organ type dust boot, and an end is set in stroke chamber 17 urceolus, and the other end is set in flywheel chamber 23 urceolus; The screw portion of hanger A16 and hanger B24 screws with stroke chamber 17 and screw thread on the 23 closed end centre holes of flywheel chamber respectively, to guarantee that two hanger center-points are on leading screw 19 axis mutually.
Below in conjunction with accompanying drawing practical implementation process of the present invention is described further.
As illustrated in fig. 1 and 2; The disturbance force that is caused by Uneven road makes left swing arm 2 down produce angular transpositions with respect to upper left swing arm 4 through tire; The generation of relative angular displacement can make left wheel vibration isolator 3 stretched and compress, and promptly left wheel vibration isolator 3 is started working, and disturbance force is attenuated; Also can be attenuated when in like manner, disturbance force is through right wheel vibration isolator 9; When upper left swing arm 4 produced angular transposition with respect to upper right swing arm 8, vehicle body vibration isolator 5 was started working, and disturbance force is attenuated again.
Shown in Fig. 3 and 4, inertial mass energy storage 15 is the input endpoint with hanger A16 and hanger B24 in the course of the work; When etc. big oppositely directed power f when being applied on two end points; Hanger A16 does straight-line motion with respect to hanger B24, by nut 18 and leading screw 19 straight-line motion is transformed rotatablely moving of leading screw, and then driving flywheel 20 rotates; Thereby the positive work that power f is done inertial mass energy storage 15 discharges when doing negative work with the stores of kinetic energy.
The kinetics equation of inertial mass energy storage is f=ba; Wherein f, a and b represent to be applied to the power on the two-end-point, the relative acceleration and the inertial mass coefficient of two-end-point respectively, and the inertial mass coefficient can be calculated by the pitch of leading screw 19 and the rotor inertia of flywheel 22.If the pitch P of leading screw 19, the rotor inertia I of flywheel 22.Can derive following relational expression by Newton's second law:
According to following formula, the pitch of change leading screw and the rotor inertia of flywheel just can obtain having the inertial mass energy storage of suitable inertial mass coefficient.
As far as the passive suspension of tradition; Adopt soft spring can suppress the low frequency peak value of vehicle body acceleration, improve the travelling comfort of vehicle, yet but make the high frequency peaks of tire live load obviously increase; Worsened the driving safety of vehicle; And adopt hard spring can suppress the high frequency peaks of tire live load, improve the driving safety of vehicle, yet but make the low frequency peak value of vehicle body acceleration obviously increase; Worsened the travelling comfort of vehicle, the traditional passive suspension that is therefore composed in parallel by spring and damper is difficult to take into account the travelling comfort and the driving safety of vehicle.The present invention adopts left and right vehicle body vibration isolator and the series connected form of wheel spacer; The low frequency peak value that suppresses vehicle body acceleration with the vehicle body vibration isolator; The low frequency peak value that has also suppressed simultaneously moving stroke of suspension and tire live load; Suppress the high frequency peaks of tire live load with left and right wheel vibration isolator, thus effective coordination of the present invention travelling comfort and the contradiction between the driving safety of vehicle, both improved the travelling comfort of vehicle greatly; Improved driving safety again, the overall performance of suspension is greatly improved.
The mode that the present invention adopts left and right suspension to connect has reduced the suspension height, makes suspension frame structure compact, is easy to arrange; The vehicle body vibration isolator adopts the form of spring, damper and the parallel connection of inertial mass energy storage; Come balance vehicle body gravity with spring; Damper and inertial mass energy storage are worked near balance position, overcome the inertial mass energy storage under the vehicle body action of gravity easily by the technical disadvantages of " puncture ".
Claims (2)
1. a through inertial mass accumulation of energy suspension is characterized in that, comprises suspension crossbeam (1), left side swing arm (2) down, left wheel vibration isolator (3), upper left swing arm (4), vehicle body vibration isolator (5), upper right swing arm (8), right wheel vibration isolator (9) and bottom right swing arm (10);
Said suspension crossbeam (1) is connected with vehicle body (6) through two fixed links (7);
Swing arm under the said left side (2) and the coaxial left end that is articulated in suspension crossbeam (1) of upper left swing arm (4); Swing arm under the said left side (2) and upper left swing arm (4) are around the hinge axis swing of suspension crossbeam (1) left end; Said bottom right swing arm (10) and the coaxial right-hand member that is articulated in suspension crossbeam (1) of upper right swing arm (8), said bottom right swing arm (10) and upper right swing arm (8) are around the hinge axis swing of suspension crossbeam (1) right-hand member; Said upper left swing arm (4) and upper right swing arm (8) are vertical when balance position;
Said left wheel vibration isolator (3) is composed in parallel by spring A (11) and damper A (12); The upper end of the upper end of said left wheel vibration isolator (3) and upper left swing arm (4) is hinged, and the lower end of said left wheel vibration isolator (3) is articulated in the position in swing arm (2) outside down, a left side with left swing arm (2) down; Said right wheel vibration isolator (9) is identical with left wheel vibration isolator (3) to be composed in parallel by spring A (11) and damper A (12); The upper end of the upper end of said right wheel vibration isolator (9) and upper right swing arm (8) is hinged, and the lower end of said right wheel vibration isolator (9) and bottom right swing arm (10) are articulated in the position in bottom right swing arm (10) outside;
Said vehicle body vibration isolator (5) is composed in parallel by spring B (13), damper B (14) and inertial mass energy storage (15), and the two ends of said vehicle body vibration isolator (5) are hinged with the upper end of the upper end of upper left swing arm (4) and upper right swing arm (8) respectively.
2. through inertial mass accumulation of energy suspension according to claim 1; It is characterized in that; Said spring A (11) and spring B (13) are spiral compression spring; Said damper A (12) and damper B (14) are the cylinder type hydraulic damper, and said inertial mass energy storage (15) is a ball-screw inertial mass energy storage.
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| Application Number | Priority Date | Filing Date | Title |
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| CN2010102813361A CN101954847B (en) | 2010-09-14 | 2010-09-14 | Through type inertial mass energy storage suspension |
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| CN2010102813361A CN101954847B (en) | 2010-09-14 | 2010-09-14 | Through type inertial mass energy storage suspension |
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| CN101954847A CN101954847A (en) | 2011-01-26 |
| CN101954847B true CN101954847B (en) | 2012-08-15 |
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| CN2010102813361A Expired - Fee Related CN101954847B (en) | 2010-09-14 | 2010-09-14 | Through type inertial mass energy storage suspension |
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| CN102494071B (en) * | 2011-11-15 | 2013-12-11 | 江苏大学 | Passive vibration isolation system for dampers of ceilings and sheds |
| CN103273817A (en) * | 2013-05-10 | 2013-09-04 | 江苏大学 | Energy storage suspension with left suspension and right suspension being communicated |
| CN103303085A (en) * | 2013-06-14 | 2013-09-18 | 江苏大学 | Vehicle passive suspension structure employing inertial container |
| CN103625233A (en) * | 2013-11-12 | 2014-03-12 | 江苏大学 | Integrated Inerter suspension for vehicle |
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| CN104455203A (en) * | 2014-11-19 | 2015-03-25 | 江苏大学 | Inertial container with two-level adjustable inertial mass coefficients |
| CN108458036B (en) * | 2018-04-23 | 2020-01-10 | 东北大学 | Vibration damper |
| CN109080399B (en) * | 2018-07-30 | 2021-10-12 | 江苏大学 | Hybrid electromagnetic suspension capable of realizing self-energy supply and control method thereof |
| CN109291757A (en) * | 2018-11-19 | 2019-02-01 | 南京农业大学 | A kind of vehicle pendulum-type suspension system |
| KR102543950B1 (en) * | 2019-10-10 | 2023-06-14 | 리 오토모티브 리미티드 | Dual-axle wheels suspension |
| CN112591663A (en) * | 2020-11-13 | 2021-04-02 | 机械工业第九设计研究院有限公司 | Automatic handling system based on AGV and multi-AGV cooperation method |
| CN113844227A (en) * | 2021-10-12 | 2021-12-28 | 安徽江淮汽车集团股份有限公司 | Inertial energy storage suspension |
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| US4573702A (en) * | 1982-03-23 | 1986-03-04 | Klem Richard H | Anti-pitch suspension |
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| CN101774341A (en) * | 2009-01-13 | 2010-07-14 | 重庆工商大学 | Vehicle suspension bracket with motion transformation spiral fly wheel |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| JP2010038240A (en) * | 2008-08-05 | 2010-02-18 | Jtekt Corp | Electromagnetic shock absorber |
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- 2010-09-14 CN CN2010102813361A patent/CN101954847B/en not_active Expired - Fee Related
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|---|---|---|---|---|
| US4573702A (en) * | 1982-03-23 | 1986-03-04 | Klem Richard H | Anti-pitch suspension |
| DE19717418C1 (en) * | 1997-04-25 | 1998-10-22 | Daimler Benz Ag | Multi-lane curve headed vehicle |
| CN101327722A (en) * | 2008-06-05 | 2008-12-24 | 江苏大学 | Vehicle suspension fork with inertia energy accumulator |
| CN101774341A (en) * | 2009-01-13 | 2010-07-14 | 重庆工商大学 | Vehicle suspension bracket with motion transformation spiral fly wheel |
| CN101670764A (en) * | 2009-09-01 | 2010-03-17 | 关国铭 | Automobile suspension system capable of generating negative-value inclination angle |
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| Title |
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Application publication date: 20110126 Assignee: NANJING GOLDEN DRAGON BUS CO., LTD. Assignor: Jiangsu University Contract record no.: 2015320000266 Denomination of invention: Through type inertial mass energy storage suspension Granted publication date: 20120815 License type: Exclusive License Record date: 20150421 |
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