WO2019144652A1 - 一种单涡轮回收能量的串串联r式汽车减振器与方法 - Google Patents

一种单涡轮回收能量的串串联r式汽车减振器与方法 Download PDF

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WO2019144652A1
WO2019144652A1 PCT/CN2018/110450 CN2018110450W WO2019144652A1 WO 2019144652 A1 WO2019144652 A1 WO 2019144652A1 CN 2018110450 W CN2018110450 W CN 2018110450W WO 2019144652 A1 WO2019144652 A1 WO 2019144652A1
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turbine
check valve
port
series
capillary
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English (en)
French (fr)
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容强
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South China University of Technology SCUT
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South China University of Technology SCUT
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B13/00—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates
    • 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
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
    • B60G13/02—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally
    • B60G13/06—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type
    • B60G13/08—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type hydraulic
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
    • B60G13/16—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dynamic absorbers as main damping means, i.e. spring-mass system vibrating out of phase
    • B60G13/18—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dynamic absorbers as main damping means, i.e. spring-mass system vibrating out of phase combined with energy-absorbing means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G15/00—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type
    • B60G15/02—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring
    • B60G15/06—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper
    • 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
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
    • F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
    • 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
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
    • F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
    • F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
    • F16F9/19—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein with a single cylinder and of single-tube type
    • 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
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
    • F16F9/466—Throttling control, i.e. regulation of flow passage geometry
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2300/00—Indexing codes relating to the type of vehicle
    • B60G2300/60—Vehicles using regenerative power
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2220/00—Application
    • F05B2220/60—Application making use of surplus or waste energy
    • F05B2220/602—Application making use of surplus or waste energy with energy recovery turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2220/00—Application
    • F05B2220/70—Application in combination with
    • F05B2220/706—Application in combination with an electrical generator
    • 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
    • F16F2222/00—Special physical effects, e.g. nature of damping effects
    • F16F2222/12—Fluid damping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
    • F16F2228/04—Frequency effects
    • 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
    • F16F2230/00—Purpose; Design features
    • F16F2230/0005—Attachment, e.g. to facilitate mounting onto confer adjustability
    • 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
    • F16F2230/00—Purpose; Design features
    • F16F2230/18—Control arrangements
    • 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
    • F16F2232/00—Nature of movement
    • F16F2232/08—Linear

Definitions

  • the invention relates to the field of hydraulic automobile dampers, in particular to a series-series R-type automobile damper and method for recovering energy by a single turbine.
  • the vibration reduction methods of automobiles mainly include hydraulic type, pneumatic type and electromagnetic type.
  • Hydraulic is the most widely used method of vibration reduction in automobiles.
  • the hydraulic oil in the hydraulic damper needs to generate damping during the oscillation process, and the process of generating the damping is a process that requires energy consumption.
  • the energy consumed by this oscillation process is called the oscillation energy.
  • the oscillating energy consumption of the hydraulic damper is wasted energy, because there is no oscillating energy recovery device in the hydraulic damper.
  • this is a damper with a natural frequency of a matrix string series capillary variable system. It includes the frame, spring, cylinder, oil tank, piston, lower oil tank, axle, adjustment section, and frequency band.
  • the adjustment section consists of a series of 4-way capillary and solenoid valves. These 4-way capillaries are all M-shaped.
  • the four capillary tubes are respectively capillary R8, R4, R2, and R1; their cross-sectional areas are equal and the solenoid valves V R8 , V R4 , V R2 , and V R1 are respectively connected in parallel.
  • the ratio of the lengths of the four capillary tubes is 8:4:2:1; that is, their lengths are arranged according to the binary encoding rule of 8421.
  • the damping can be adjusted by adjusting the configuration S Rn of the solenoid valves V R8 , V R4 , V R2 , V R1 .
  • the tuning frequency band consists of a series of 4-way capillary and solenoid valves. These 4-way capillaries are all M-shaped.
  • the four capillary tubes are capillary tubes m8, m4, m2, and m1, respectively; their cross-sectional areas are equal and the solenoid valves V m8 , V m4 , V m2 , and V m1 are respectively connected in parallel.
  • the ratio of the lengths of the four capillary tubes is 8:4:2:1; that is, their lengths are arranged according to the binary encoding rule of 8421.
  • the diameter d m of the four-way capillary is more than twice the capillary diameter d R of the regulation section.
  • the natural frequency of the system can be adjusted by adjusting the configuration S mn of the solenoid valves V m8 , V m4 , V m2 , V m1 .
  • the object of the present invention is to overcome the above-mentioned shortcomings and shortcomings of the prior art, and to provide a series-series R-type automobile damper and method for recovering energy by a single turbine, and to solve the problem that the oscillation energy consumption cannot be recovered.
  • a series-connected R type automobile damper with single turbine recovery energy comprising a frame 1, an axle 7 and a hydraulic cylinder 3; an upper end of the hydraulic cylinder 3 is connected to the frame 1 through a piston rod thereof, and a lower end cylinder of the hydraulic cylinder 3
  • the body is connected to the axle 7; the piston 5 in the hydraulic cylinder 3 divides the hydraulic cylinder 3 into an upper oil tank 4 and a lower oil tank 6; on the pipeline between the upper oil tank 4 and the lower oil tank 6 oil supply port,
  • the upper and lower sections are connected with a regulation section, a frequency modulation band, and a single turbine energy recovery section; that is, the F port of the adjustment section is connected to the A port of the oil tank 4, and the E port of the adjustment section is connected to the frequency modulation zone I.
  • a single turbine energy recovery section is disposed on the oil passage between the oil port, the J port of the frequency band and the B port of the lower oil tank 6;
  • the single turbine energy recovery section includes: a check valve V 6 , a check valve V 3 , a check valve V 4 , a check valve V 5 , a turbine T, and a generator G;
  • the inlet of the turbine T is respectively connected to the outlet of the check valve V 3 and the outlet of the check valve V 5 through the O-way;
  • the outlet of the turbine T is respectively connected to the inlet of the check valve V 6 and the inlet of the check valve V 4 through the P-way pipe;
  • the inlet of the one-way valve V 3 and the outlet of the one-way valve V 6 are connected to the J port of the frequency modulation band through the M three-way pipe;
  • the outlet of the one-way valve V 4 and the inlet of the one-way valve V 5 are connected to the B port of the lower oil tank 6 through the N-way pipe;
  • the drive shaft of the turbine T is coupled to the rotor of the generator.
  • the modulating section comprises four capillary tubes connected in series; the four capillary tubes are all connected with a solenoid valve in parallel;
  • the tuning frequency band includes four capillary tubes connected in series; the four capillary tubes are all connected with a solenoid valve in parallel.
  • the two interface ends of the frequency modulation band are respectively an I port and a J port.
  • the four-way capillary cross-sectional area of the modulation band is equal.
  • the ratio of the lengths of the four capillary tubes of the modulation band is 8:4:2:1; that is, their lengths are arranged according to the binary coding rule of 8421.
  • the diameter d m of the capillary is more than twice the capillary diameter d R of the adjustment section.
  • the capillaries in the modulating section and the tuning band are all in an "M” shape, an "S” shape or a spiral shape.
  • the solenoid valve in the adjustment section and the modulation frequency band is also connected to the control system; the control system is used to control the on and off of each solenoid valve.
  • a spring 2 is arranged between the frame 1 and the axle 7.
  • the energy recovery method of the tandem series R type automobile damper of the single turbine recovery energy of the present invention is as follows:
  • the hydraulic oil flows from the oil port of the upper oil tank 4 through the regulating section, the frequency modulation band, the check valve V 3 , the turbine T, the check valve V 4 into the lower oil tank 6;
  • the hydraulic oil flows from the B port of the lower oil tank 6 through the check valve V 5 , the turbine T, the check valve V 6 , the frequency modulation band, and the adjustment section into the upper oil storage tank 4;
  • the present invention has the following advantages and effects:
  • the invention has the advantages of ingenious design, low cost and convenient technical means.
  • the generator is driven to generate electricity, which solves the problem that the oscillating energy consumption of the automobile damper cannot be recovered; at the same time, the operating temperature of the hydraulic oil can be lowered and the service life of the damper can be improved.
  • the invention has positive and outstanding beneficial effects on the development of modern automobile vibration damping technology.
  • FIG. 1 is a schematic structural view of a damper of a natural frequency of a conventional matrix string series capillary variable system.
  • Figure 2 is a schematic view of the structure of the present invention.
  • the regulating section includes four capillary tubes which are respectively R8, R4, R2 and R1; their cross-sectional areas are equal and the parallel solenoid valves V R8 , V R4 , V R2 , V R1 respectively control their operation.
  • the ratio of the lengths of the four capillary tubes is 8:4:2:1; their diameters are both d R .
  • the tuning frequency band includes four capillary tubes respectively m8, m4, m2, m1; their cross-sectional areas are equal and the parallel solenoid valves V m8 , V m4 , V m2 , V m1 respectively control their operation; the ratio of the length of the four capillary tubes is 8 :4:2:1.
  • the length L m1 of the shortest capillary m1 of the four-way capillary is equal to half the length L R8 of the longest capillary R8 of the modulating section.
  • the diameter d m of the four-way capillary is equal to 4 times d R .
  • the single turbine energy recovery section includes a check valve V 3 , a check valve V 4 , a check valve V 5 , a check valve V 6 , a turbine T, and a generator G.
  • the piston When the relative movement between the frame and the axle occurs, the piston will correspondingly move up or down; the upward movement of the piston is the extension stroke, and the downward movement of the piston is the compression stroke.
  • the hydraulic oil in the hydraulic cylinder 3 will pass through the adjustment section between the A port and the B port, the frequency modulation band, the single turbine energy recovery section, and then flow from the upper oil tank 4 to the oil tank 6 or from the oil.
  • the bin 6 flows up to the oil bunker 4.
  • the capillary working in the adjustment section will dampen the flow of the hydraulic oil, thereby forming a damping of the movement of the piston; the magnitude of the damping is controlled by The system is controlled by the configuration of the solenoid valve S Rn , thereby realizing the adjustment of the adjustment section;
  • the configuration S mn of the electromagnetic valve is changed by the control system, and the natural frequency of the system of the damper can be adjusted, thereby realizing the frequency modulation of the frequency modulation band;
  • the generator G When the hydraulic oil passes through the single turbine energy recovery section, according to the flow direction of the hydraulic oil, or the hydraulic oil flows from the M tee through the check valve V 3 , the turbine T, the check valve V 4 to the lower oil tank 6 while the turbine T is towed
  • the generator G generates electricity to realize the oscillation energy recovery of the extension stroke; or the hydraulic oil flows from the lower oil tank 6 through the check valve V 5 , the turbine T, the check valve V 6 to the M three-way pipe, and the turbine T drags the power generation.
  • the machine G generates electricity and realizes the recovery of the oscillation energy consumption of the compression stroke; thus, we solve the problem that the oscillation energy cannot be recovered.
  • connection sequence of the regulation section, the modulation frequency band, and the single-turbine energy recovery section can be connected according to the frequency modulation band, the single-turbine energy recovery section, and the adjustment section, in addition to the sequence as shown in FIG. 2, and of course, the single-turbine energy can also be used.
  • the recycling section, the adjustment section, the tuning frequency band, and the like are sequentially connected.
  • the resistance of the damper is adjusted by the control of the control system using the capillary tubes R8, R4, R2, R1 and their corresponding solenoid valves. It is characterized in that, in addition to the cylinder block, depending on the resistance characteristics of the capillary, multiple (may be four or non-four) capillaries in series (or in parallel) can be determined according to specific parameters (eg area, Or the length, or the flow resistance of the hydraulic oil under certain working conditions, etc.) are arranged according to certain rules (for example: binary coding rules of 8421, or other equal ratio or non-equal ratio rules), through the control system to the corresponding capillary
  • the solenoid valve is controlled to achieve the purpose of adjusting the damping. These are the meanings of the "R-type" in the adjustment section.
  • the natural frequency of the damper system is adjusted under the control of the control system with the capillary m8, m4, m2, m1 and their corresponding solenoid valves.
  • the utility model is characterized in that: in the outside of the cylinder block, when the diameter of the capillary tube is large, the resistance is small, and depending on the capacity characteristic of the capillary, the multiple paths in series (or parallel) may be four or four.
  • the capillary is arranged according to certain parameters (such as: area, length, or volume, etc.) according to certain rules (such as: the binary coding rule of the 8421 ratio, or other equal ratio or non-equal ratio rule), through the control system
  • the solenoid valve of the corresponding capillary is controlled to achieve the purpose of adjusting the natural frequency of the damper system by adjusting the quality of the hydraulic oil participating in the oscillation.
  • R-type damper When the damper has any of the above two "R-type” meanings, we will call it R-type damper or R-type automobile damper.
  • R-type damper when there are both the capillary adjustment section and the capillary adjustment frequency band, the number of the adjustment section and the modulation band capillary may be equal or different.
  • the capillary of the R type damper can be processed into a spiral shape or an "S" shape in addition to the "M" shape. These shapes are only a few of the specific shapes listed, and many shapes can be listed in practical applications, which can be flexibly determined according to specific requirements.
  • the capillary does not have to be so fine.
  • the so-called thin means that the hydraulic oil will flow through the capillary. That is to say, the capillary is the resistance generated when the hydraulic oil flows. Tubing or oil circuit.
  • the present invention can be preferably implemented.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Vibration Prevention Devices (AREA)
  • Vehicle Body Suspensions (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

一种单涡轮回收能量的串串联R式汽车减振器与方法，在其上油仓（4）和下油仓（6）输油口之间的管路上，串联有串联毛细管调阻段、串联毛细管调频段、单涡轮能量回收段。单涡轮能量回收段包括：单向阀V6、单向阀V3、单向阀V4、单向阀V5、涡轮T和发电机G。当液压油由上油仓（4）的A油口依次流经调阻段、调频段、单向阀V3、涡轮T、单向阀V4进入下油仓（6）时，液压油推动涡轮T，涡轮T驱动发电机G发电，实现伸张行程的振荡耗能回收，相应地，减振器也可以实现压缩行程的振荡耗能回收。

Description

一种单涡轮回收能量的串串联R式汽车减振器与方法 技术领域
本发明涉及液压式汽车减振器领域，尤其涉及一种单涡轮回收能量的串串联R式汽车减振器与方法。
背景技术
汽车的减振方式主要有液压式、气压式、电磁式。液压式是目前用得最广泛的汽车减振方式。液压式减振器中的液压油在振荡过程中需要产生阻尼，而产生阻尼的过程是一个需要消耗能量的过程。我们将该振荡过程消耗掉的能量称为振荡耗能。目前，液压式减振器的振荡耗能是浪费掉的能量，其原因是液压减振器中没有振荡耗能回收装置。
如图1所示，这是一个矩阵串串联毛细管可变系统固有频率的减振器。它包括车架、弹簧、缸体、上油仓、活塞、下油仓、车轴、调阻段、调频段。
调阻段由串联的4路毛细管、电磁阀组成。这4路毛细管都盘成了M型。这4路毛细管分别是毛细管R8、R4、R2、R1；它们的截面积相等且分别并联电磁阀V R8、V R4、V R2、V R1。这4路毛细管的长度之比是8:4:2:1；即它们的长度是按照8421的二进制编码规则来排列的。调节电磁阀V R8、V R4、V R2、V R1的组态S Rn即可调节阻尼。
调频段由串联的4路毛细管、电磁阀组成。这4路毛细管都盘成了M型。这4路毛细管分别是毛细管m8、m4、m2、m1；它们的截面积相等且分别并联电磁阀V m8、V m4、V m2、V m1。这4路毛细管的长度之比是8:4:2:1；即它们的长度是按照8421的二进制编码规则来排列的。这四路毛细管的直径d m大于调阻段的毛细管直径d R一倍以上。调节电磁阀V m8、V m4、V m2、V m1的组态S mn即可调节系统固有频率。
在如图1所示的液压式减振器中，因为没有振荡耗能回收装置，所以存 在着振荡耗能无法回收的问题。
发明内容
本发明的目的在于克服上述现有技术的缺点和不足，提供一种单涡轮回收能量的串串联R式汽车减振器与方法，解决振荡耗能无法回收的问题。
本发明通过下述技术方案实现：
一种单涡轮回收能量的串串联R式汽车减振器，包括车架1、车轴7和液压缸3；所述液压缸3的上端通过其活塞杆连接车架1，液压缸3的下端缸体连接车轴7；液压缸3内的活塞5将液压缸3分为上油仓4和下油仓6；其所述上油仓4和下油仓6输油口之间的管路上，自上而下依次连接有调阻段、调频段、单涡轮能量回收段；即，调阻段的F油口连接上油仓4的A油口，调阻段的E油口连接调频段的I油口，调频段的J油口与下油仓6的B油口之间的油路上设置单涡轮能量回收段；
所述单涡轮能量回收段包括：单向阀V 6、单向阀V 3、单向阀V 4、单向阀V 5、涡轮T和发电机G；
所述涡轮T的进口通过O三通管分别连通单向阀V 3的出口和单向阀V 5的出口；
所述涡轮T的出口通过P三通管分别连通单向阀V 6的进口和单向阀V 4的进口；
所述单向阀V 3的进口和单向阀V 6的出口通过M三通管连通调频段的J油口；
所述单向阀V 4的出口和单向阀V 5的进口通过N三通管连通下油仓6的B油口；
涡轮T的传动轴与发电机的转子连接。
所述调阻段包括串联的四路毛细管；这四路毛细管均并联有电磁阀；
所述调频段包括串联的四路毛细管；这四路毛细管均并联有电磁阀。
所述调频段的两个接口端分别为I油口、J油口。
所述调频段的四路毛细管截面积相等。
所述调频段的四路毛细管的长度之比是8:4:2:1；即它们的长度是按照8421的二进制编码规则来排列的。
所述调频段的四路毛细管中，毛细管的直径d m比调阻段的毛细管直径d R大一倍以上。
所述调阻段和调频段中的毛细管，均盘成“M”形状、“S”形状或者螺旋形状。
所述调阻段和调频段中的电磁阀还与控制系统连接；控制系统用于控制各电磁阀的通断。
车架1与车轴7之间设有弹簧2。
本发明单涡轮回收能量的串串联R式汽车减振器的能量回收方法如下：
伸张行程的振荡耗能回收步骤：
液压油由上油仓4的A油口依次流经调阻段、调频段、单向阀V 3、涡轮T、单向阀V 4进入下油仓6；
所述液压油在流经涡轮T的同时，涡轮T驱动发电机G的转子运转发电；实现伸张行程的振荡耗能回收；
压缩行程的振荡耗能回收步骤：
液压油由下油仓6的B油口依次流经单向阀V 5、涡轮T、单向阀V 6、调频段、调阻段进入上油仓4；
所述液压油在流经涡轮T的同时，涡轮T驱动发电机G的转子运转发电；实现压缩行程的振荡耗能回收。
本发明相对于现有技术，具有如下的优点及效果：
本发明构思巧妙、造价低廉、技术手段简便易行。通过单向阀原理与涡轮的有机结合，推动发电机发电，解决了汽车减振器的振荡耗能无法回收的问题；同时，还可以降低液压油的运行温度、提高减振器的使用寿命。本发 明对现代汽车减振技术的发展，具有积极、突出的有益效果。
附图说明
图1为现有矩阵串串联毛细管可变系统固有频率的减振器结构示意图。
图2为本发明结构示意图。
具体实施方式
下面结合具体实施例对本发明作进一步具体详细描述。
实施例
如附图2所示。
调阻段包括四路毛细管分别是R8、R4、R2、R1；它们截面积相等且分别并联电磁阀V R8、V R4、V R2、V R1控制其工作。这四路毛细管的长度之比是8:4:2:1；它们的直径均为d R。
调频段包括四路毛细管分别是m8、m4、m2、m1；它们截面积相等且分别并联电磁阀V m8、V m4、V m2、V m1控制其工作；这四路毛细管的长度之比是8:4:2:1。在本实施例中，这四路毛细管中最短毛细管m1的长度L m1等于调阻段最长毛细管R8的长度L R8的一半。这四路毛细管的直径d m等于4倍d R。
单涡轮能量回收段包括单向阀V 3、单向阀V 4、单向阀V 5、单向阀V 6、涡轮T、发电机G。涡轮T的最大流量Q Tmax比减振器最大液压油流量Q Smax大10％；即：Q Tmax＝1.1Q Smax。
当车架和车轴之间产生相对运动时，活塞会相应的产生或上或下的移动；活塞向上移动行程为伸张行程，活塞向下移动的行程为压缩行程。此时液压缸3内的液压油会经过A油口、B油口之间的调阻段、调频段、单涡轮能量回收段，进而从上油仓4流向下油仓6，或者从下油仓6流向上油仓4。
由于缸体内液压油的粘性作用，当液压油流经调阻段时，调阻段中工作的毛细管会对液压油的流动产生阻尼，从而形成对活塞移动的阻尼；该阻尼的大小由控制系统通过电磁阀的组态S Rn控制，进而实现调阻段的调阻；
当液压油流经调频段时，通过控制系统改变电磁阀的组态S mn，则可调节减振器的系统固有频率，进而实现调频段的调频；
当液压油经过单涡轮能量回收段时，根据液压油的流向，或者液压油从M三通管经过单向阀V 3、涡轮T、单向阀V 4流向下油仓6，同时涡轮T拖动发电机G发电，实现伸张行程的振荡耗能回收；或者液压油从下油仓6经过单向阀V 5、涡轮T、单向阀V 6流向M三通管，同时涡轮T拖动发电机G发电，实现压缩行程的振荡耗能回收；这样我们就解决了振荡耗能无法回收的问题。
现通过以下三点对本实施例作进一步说明。
1、关于单涡轮能量回收段的工作原理
当液压油需要从M三通管流向N三通管时，活塞向上移动，此行程为伸张行程，因为单向阀V 5、V 6的截止作用，液压油只能够从M三通管经过单向阀V 3、涡轮T、单向阀V 4流向下油仓6；同时液压油推动涡轮T的叶轮转动，涡轮T拖动发电机G发电，实现伸张行程的振荡耗能回收。
当液压油需要从N三通管流向M三通管时，活塞向下移动，此行程为压缩行程，因为单向阀V 3、V 4的截止作用，液压油只能够从N三通管经过单向阀V 5、涡轮T、单向阀V 6流向M三通管；同时液压油推动涡轮T的叶轮转动，涡轮T拖动发电机G发电，实现压缩行程的振荡耗能回收。
2、关于调阻段、调频段、单涡轮能量回收段的连接顺序
调阻段、调频段、单涡轮能量回收段的连接顺序除了按照如图2的顺序连接外，还可以按照调频段、单涡轮能量回收段、调阻段连接，当然，也可以按照单涡轮能量回收段、调阻段、调频段等顺序连接。
3、关于“单涡轮回收能量的串串联R式汽车减振器”的名称
在“单涡轮回收能量的串串联R式汽车减振器”的名称中，其“串串联”中第一个“串”表示调阻段用串联式毛细管调节、第二个“串”表示调频段用串联式毛细管调节。其“R式”表示的意义如下：
在毛细管的调阻段，用毛细管R8、R4、R2、R1及其对应的电磁阀在控 制系统的控制下对减振器的阻力(Resistance)进行调节的方式。其特点是：在液压缸缸体以外，依据毛细管的阻力(Resistance)特性，将串联(或者并联)的多路(可以是四路也可以是非四路)毛细管依据特定的参数(比如：面积、或者长度、或者某个工况下液压油的流动阻力等)按照一定的规则(比如：8421等比的二进制编码规则、或者其它等比或者非等比规则)排列，通过控制系统对相应毛细管的电磁阀进行控制从而达到调节阻尼的目的。以上这些就是在调阻段的“R式”的意义。
在调频段，因为我们利用毛细管调节频率的结构与方式与上述毛细管调节阻尼的结构与方式有很多相似之处，所以我们将利用毛细管及电磁阀达到调节减振器系统固有频率的方式也称为“R式”。在调频段，“R式”的意义具体解释如下：
在毛细管的调频段，用毛细管m8、m4、m2、m1及其对应的电磁阀在控制系统的控制下对减振器系统固有频率进行调节的方式。其特点是：在液压缸缸体以外，利用毛细管管径大时其阻力(Resistance)小的特性，依据毛细管的容量特性，将串联(或者并联)的多路(可以是四路也可以是非四路)毛细管依据特定的参数(比如：面积、或者长度、或容积等)按照一定的规则(比如：8421等比的二进制编码规则、或者其它等比或者非等比规则)排列，通过控制系统对相应毛细管的电磁阀进行控制从而达到通过调节参与振荡的液压油的质量进而达到调节减振器系统固有频率的目的。
当减振器只要具有上述两个“R式”意义中的任意一个意义时，我们就将之称为R式减振器或者R式汽车减振器。在R式减振器中，当既有毛细管调阻段也有毛细管调频段时，其调阻段、调频段毛细管的路数可以相等，也可以不等。R式减振器的毛细管除加工成“M”形状外还可以加工成螺旋形状、“S”形状等其他形状。这几种形状仅为具体所列的几种形状，在实际应用中还可罗列出很多形状，可根据具体要求灵活而定。
另外，在R式减振器中，其毛细管不一定要多么细，所谓细就是指液压油流过毛细管时会产生阻力；也就是说，我们所说的毛细管就是液压油流过 时会产生阻力的油管或者油路。
如上所述，便可较好地实现本发明。
本发明的实施方式并不受上述实施例的限制，其他任何未背离本发明的精神实质与原理下所作的改变、修饰、替代、组合、简化，均应为等效的置换方式，都包含在本发明的保护范围之内。

Claims (10)

  1. 一种单涡轮回收能量的串串联R式汽车减振器，包括车架(1)、车轴(7)和液压缸(3)；所述液压缸(3)的上端通过其活塞杆连接车架(1)，液压缸(3)的下端缸体连接车轴(7)；液压缸(3)内的活塞(5)将液压缸(3)分为上油仓(4)和下油仓(6)；其特征在于：所述上油仓(4)和下油仓(6)输油口之间的管路上，自上而下依次连接有调阻段、调频段、单涡轮能量回收段；即，调阻段的F油口连接上油仓(4)的A油口，调阻段的E油口连接调频段的I油口，调频段的J油口与下油仓(6)的B油口之间的油路上设置单涡轮能量回收段；
    所述单涡轮能量回收段包括：单向阀V 6、单向阀V 3、单向阀V 4、单向阀V 5、涡轮T和发电机G；
    所述涡轮T的进口通过O三通管分别连通单向阀V 3的出口和单向阀V 5的出口；
    所述涡轮T的出口通过P三通管分别连通单向阀V 6的进口和单向阀V 4的进口；
    所述单向阀V 3的进口和单向阀V 6的出口通过M三通管连通调频段的J油口；
    所述单向阀V 4的出口和单向阀V 5的进口通过N三通管连通下油仓(6)的B油口；
    涡轮T的传动轴与发电机的转子连接。
  2. 根据权利要求1所述单涡轮回收能量的串串联R式汽车减振器，其特征在于：
    所述调阻段包括串联的四路毛细管，这四路毛细管均并联有电磁阀；
    所述调频段包括串联的四路毛细管；这四路毛细管均并联有电磁阀。
  3. 根据权利要求2所述单涡轮回收能量的串串联R式汽车减振器，其特征在于：所述调频段的两个接口端分别为I油口、J油口。
  4. 根据权利要求2所述单涡轮回收能量的串串联R式汽车减振器，其特征在于：所述调频段的四路毛细管截面积相等。
  5. 根据权利要求2所述单涡轮回收能量的串串联R式汽车减振器，其特征在于：所述调频段的四路毛细管的长度之比是8:4:2:1；即它们的长度是按照8421的二进制编码规则来排列的。
  6. 根据权利要求5所述单涡轮回收能量的串串联R式汽车减振器，其特征在于：所述调频段的四路毛细管中，毛细管的直径d m比调阻段的毛细管直径d R大一倍以上。
  7. 根据权利要求1至6中任一项所述单涡轮回收能量的串串联R式汽车减振器，其特征在于：所述调阻段和调频段中的毛细管，均盘成“M”形状、“S”形状或者螺旋形状。
  8. 根据权利要求7所述单涡轮回收能量的串串联R式汽车减振器，其特征在于：所述调阻段和调频段中的电磁阀还与控制系统连接；控制系统用于控制各电磁阀的通断。
  9. 根据权利要求7所述单涡轮回收能量的串串联R式汽车减振器，其特征在于：车架(1)与车轴(7)之间设有弹簧(2)。
  10. 权利要求7所述单涡轮回收能量的串串联R式汽车减振器的能量回 收方法，其特征在于包括如下步骤：
    伸张行程的振荡耗能回收步骤：
    液压油由上油仓(4)的A油口依次流经调阻段、调频段、单向阀V 3、涡轮T、单向阀V 4进入下油仓(6)；
    所述液压油在流经涡轮T的同时，涡轮T驱动发电机G的转子运转发电；实现伸张行程的振荡耗能回收；
    压缩行程的振荡耗能回收步骤：
    液压油由下油仓(6)的B油口依次流经单向阀V 5、涡轮T、单向阀V 6、调频段、调阻段进入上油仓(4)；
    所述液压油在流经涡轮T的同时，涡轮T驱动发电机G的转子运转发电；实现压缩行程的振荡耗能回收。
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