WO2015081814A1 - 具有扭转减振功能的电涡流缓速器 - Google Patents

具有扭转减振功能的电涡流缓速器 Download PDF

Info

Publication number
WO2015081814A1
WO2015081814A1 PCT/CN2014/092515 CN2014092515W WO2015081814A1 WO 2015081814 A1 WO2015081814 A1 WO 2015081814A1 CN 2014092515 W CN2014092515 W CN 2014092515W WO 2015081814 A1 WO2015081814 A1 WO 2015081814A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
eddy current
current retarder
torsional vibration
vibration damper
Prior art date
Application number
PCT/CN2014/092515
Other languages
English (en)
French (fr)
Inventor
王占彬
侯俊剑
王亚奎
张博强
谢富科
魏亚鹏
Original Assignee
郑州宇通客车股份有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 郑州宇通客车股份有限公司 filed Critical 郑州宇通客车股份有限公司
Publication of WO2015081814A1 publication Critical patent/WO2015081814A1/zh

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L7/00—Electrodynamic brake systems for vehicles in general
    • B60L7/28—Eddy-current braking
    • 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
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K49/00—Dynamo-electric clutches; Dynamo-electric brakes
    • H02K49/02—Dynamo-electric clutches; Dynamo-electric brakes of the asynchronous induction type
    • H02K49/04—Dynamo-electric clutches; Dynamo-electric brakes of the asynchronous induction type of the eddy-current hysteresis type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L2220/00—Electrical machine types; Structures or applications thereof
    • B60L2220/10—Electrical machine types
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L2270/00—Problem solutions or means not otherwise provided for
    • B60L2270/10—Emission reduction
    • B60L2270/14—Emission reduction of noise
    • B60L2270/145—Structure borne vibrations
    • 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
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/129—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by friction-damping means
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/64—Electric machine technologies in electromobility

Definitions

  • the present invention relates to an automotive brake device, and more particularly to an eddy current retarder having a torsional vibration damper function.
  • the eddy current retarder is a vehicle auxiliary braking device, generally composed of a stator, a stator bracket and a rotor coaxially arranged on both sides of the stator, and is often installed between the automobile drive axle and the gearbox, and is realized by the principle of electromagnetic induction. Contact brake.
  • the stator coil is energized to generate a magnetic field.
  • the rotor rotating with the drive shaft will cut the magnetic lines generated by the stator, thereby generating a vortex-like induced current inside the rotor disk, and the stator will be turned to the rotor.
  • An electromagnetic force that impedes the rotation of the rotor is applied to generate a braking torque to form a braking effect.
  • the eddy current retarder can effectively improve the braking safety of passenger cars, trucks and other vehicles.
  • the eddy current retarder rotor has a large moment of inertia and is directly connected in series in the transmission system, the inertial force shock generated by the fluctuation of the rotor speed directly acts on the transmission system of the vehicle, and the NVH performance and components of the vehicle transmission system (especially It is a new requirement for the fatigue life of the rear axle).
  • the retarder braking before the braking force comes from the rear axle final drive, the braking torque is reversed from the driving torque.
  • the driven gear of the main reducer rotates faster than the driving gear, which leads to the main
  • the passive gear is in the meshing state of the back of the tooth. Due to the large reaction torque and the precision of the main reduction of the back teeth, the rear axle is easy to generate large vibration and noise.
  • the instantaneous braking torque acts on the drive train. It will have a large impact on the gearbox gear, especially the rear axle gear, which will aggravate the vibration noise of the rear axle and affect the service life of the rear axle.
  • the retarder is not braking, the vehicle will be in the process of high-speed taxiing.
  • the rear axle gear drags the drive shaft and the retarder rotor.
  • the rear axle gear load fluctuates greatly, which is easy to cause rear axle vibration and noise.
  • the retarder rotor will generate acceleration with the rapid change of engine speed and torque, due to the large moment of inertia of the retarder rotor and the clearance of the shaft assembly of the rear axle of the drive shaft.
  • Retarder rotor have a greater impact torsional force is directly transmitted to the rear axle a gear train, so that the main reduction gear Rear axle gear back transient contact force increase, thereby generating large vibration and noise.
  • the eddy current retarder improves the braking safety performance of the vehicle, it also has many negative effects on the comfort of the whole vehicle. Therefore, it is necessary to optimize the retarder structure and increase the corresponding vibration and noise control measures.
  • an eddy current retarder with torsional vibration damper function of the present invention adopts the following technical solution: an eddy current retarder having a torsional vibration damper function, including a stator, an upstream rotor for connecting with a vehicle gearbox, and A downstream rotor for connecting to a front axle drive shaft of the vehicle, the downstream rotor being provided with a damping buffer for connecting to a front axle drive shaft of the vehicle rear axle.
  • the damping buffer device includes a driven hub disposed coaxially with the downstream rotor, the driven hub and the downstream rotor being coupled between the rotor and having a relative rotational margin therebetween, the downstream rotor and the driven hub An elastic cushion member for buffering an impact generated by relative rotation between the two is provided.
  • the rotational margin between the driven hub and the downstream rotor is formed by the gap between the pin and the corresponding pin bore.
  • the elastic cushioning member is a coil spring that is placed between the downstream rotor and the driven hub, and the center line of the coil spring vertically intersects the centerline space of the downstream rotor.
  • the downstream rotor includes an inner disk and an outer disk fixed together, and the outer disk and the driven disk hub are provided with mutually corresponding spring window holes, and the coil springs are disposed in the spring window holes of the outer disk and the driven disk hub, The outer disk and the driven hub are spanned together on the coil spring in the radial direction of the coil spring.
  • the outer side of the driven hub is provided with a spring chuck, and the coil spring is assembled in the corresponding spring window hole by the spring chuck.
  • a damping damping pad is disposed between the driven hub and the downstream rotor and/or between the spring chucks.
  • a damping damping pad is disposed between the driven hub and the downstream rotor.
  • the downstream rotor is a non-brake rotor that does not generate a braking force.
  • the downstream rotor is a non-brake rotor that does not generate a braking force.
  • the eddy current retarder since the downstream rotor is provided with a vibration damping buffer device for connecting with the front end transmission shaft of the vehicle rear axle, the torsional counter moment generated instantaneously acts on the vibration damping buffer device during operation. Through the buffering and damping action of the vibration damping device, the instantaneous torque shock is reduced, thereby reducing the impact and reducing the vibration. In addition, when the retarder is not braking, the vibration damping device is connected in series. In the system, it is beneficial to attenuate the torque fluctuation caused by the angle between the engine and the shafting space, and improve the NVH performance of the drive train. In summary, the eddy current retarder can reduce the vibration and noise that the retarder brings to the vehicle.
  • the driven hub is for facilitating the setting of the elastic buffer member, and at the same time is used as the interface to output power;
  • the coil spring is used as the elastic buffer member to facilitate the adjustment of the elastic stiffness;
  • the vibration damping spacer is for the vibration damping disc.
  • Figure 1 is a front elevational view of an embodiment of an eddy current retarder having a torsional vibration damper function
  • Figure 2 is a left side elevational view of an embodiment of an eddy current retarder having a torsional vibration damper function
  • FIG 3 is an exploded view of the downstream rotor and the vibration damping device.
  • the eddy current retarder having a torsional vibration damper function includes a stator 11, an upstream rotor 12, and a downstream rotor 13, and an upstream rotor 12
  • the downstream rotor 13 is for connection to a front axle drive shaft of the vehicle. Further, the downstream rotor 13 is provided with a vibration damping device for connecting to the front end drive shaft of the vehicle rear axle.
  • the downstream rotor 13 is composed of an inner disk 131 and an outer disk 132 which are fixed together, and a gap is provided between the inner and outer disks, and the two are connected by some connecting ribs at the edges, and the power is connected. It is transmitted from the upstream rotor 12 to the outer disk 132 through the inner disk 131.
  • the damping buffer device includes a driven hub 14 disposed coaxially with the downstream rotor 13. The coaxiality can be determined by the inner bore 24 of the outer disc 132 and the inner flange of the driven hub 14, and the outer disc 132 and the spring chuck 18 pass through the rivet holes.
  • the clearance margin determines the relative rotation angle between the rotor hub 14 and the outer disk 132.
  • the outer disk 132 and the rotor hub 14 are connected by an elastic buffer member, and the elastic buffer member is a coil spring 16 (other implementations)
  • the elastic buffer member is a coil spring 16 (other implementations)
  • a secondary damping spring, an elastic rubber, or the like formed by connecting a large spring and a small spring in parallel may be used.
  • the center line of the coil spring 16 vertically intersects the center line space of the downstream rotor 13, and in order to realize the mounting of the coil spring 16,
  • the outer disk 132 and the driven hub 14 of the downstream rotor 13 are provided with mutually corresponding spring window holes 17, which are disposed in the spring holes of the outer disk 132 and the driven disk hub 14, wherein the outer disk 132 and the driven disk hub 14 total cross-helical spring 16 in the radial half, under
  • the flange on the outer disk bolt window of the rotor 13 can block the coil spring 16 from coming out from the inner side of the outer disk.
  • the driven hub 14 and the spring chuck 18 span the other half of the radial direction of the coil spring 16, and the coil spring 16 passes through the spring chuck 18.
  • the outer retaining fit is assembled in the corresponding spring window opening.
  • the spring chuck 18 has an opening corresponding to the spring window opening, but the opening has an outwardly folded flange 19 and a flange 19
  • the coil springs 16 are confined in the corresponding spring window holes in a riveted manner, thereby achieving outward prevention of the coil springs 16.
  • a vibration damping spacer 20 is further disposed between the driven hub and the downstream rotor and between the spring chuck, and the damping damping spacer 20 is for damping the hub and the downstream.
  • the friction between the rotor and the spring chuck consumes torsional vibration energy to rapidly attenuate the torsional vibration.
  • the downstream rotor 13 is a non-brake rotor that does not generate a braking force. This can be done by changing the winding of the stator coil It is realized that magnetic force lines are generated only at one end (upstream rotor end) to generate a braking effect, and the other end (downstream rotor end) is free of magnetic lines, that is, no braking effect.
  • the power is transmitted from the upstream rotor 12 to the downstream rotor 13, and the rotor 13 transmits the damped power to the driven hub 14 through the coil spring 16, and then passes through the flange interface 23 on the moving coil hub 14 to Rear axle drive shaft.

Landscapes

  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Braking Arrangements (AREA)
  • Dynamo-Electric Clutches, Dynamo-Electric Brakes (AREA)

Abstract

一种具有扭转减振功能的电涡流缓速器，包括定子（11）、用于与车辆变速箱连接的上游转子（12）和用于与后桥前端传动轴连接的下游转子（13），所述下游转子（13）上设有用于与后桥前端传动轴连接的减振缓冲装置。在工作时，瞬间产生的扭转反力矩作用于减振缓冲装置上，通过减振缓冲装置的缓冲及衰减作用，将瞬间产生的扭矩冲击减小，从而可达到减小冲击、减轻振动的目的，另外，在缓速器不制动时，减振缓冲装置串联在传动系统中，有利于衰减由发动机和轴系空间夹角产生的扭矩波动，提升传动系的NVH性能。综上所述，该电涡流缓速器能够减小缓速器给车辆带来的振动和噪音。

Description

具有扭转减振功能的电涡流缓速器 技术领域
本发明涉及汽车制动装置，特别是涉及到一种具有扭转减振功能的电涡流缓速器。
背景技术
电涡流缓速器是一种车辆辅助制动装置，一般由定子、定子支架和同轴设于定子两侧的转子组成，常安装在汽车驱动桥与变速箱之间，通过电磁感应原理实现无接触制动。当缓速器工作时，定子线圈内通电产生磁场，此时随传动轴一起旋转的转子将会切割定子产生的磁力线，从而在转子盘内部产生涡旋状的感应电流，同时定子就会向转子施加一个阻碍转子旋转的电磁力，进而产生制动力矩，形成制动效果。
电涡流缓速器能有效改善客车、货车等车辆的制动安全性。但由于电涡流缓速器转子转动惯量比较大，并且是直接串联在传动系统中，转子转速的波动产生的惯性力冲击直接作用于车辆的传动系统，对车辆传动系统NVH性能和零部件(特别是后桥)的疲劳寿命提出了新的要求。一方面，在缓速器制动时，制动力来自于后桥主减速器之前，制动力矩与驱动力矩反向，此时主减速机的被动齿轮转动速度高于主动齿轮转速，进而导致主、被动齿轮处于齿背面啮合状态，由于较大的反作用力矩以及主减背齿啮合精度使得此时后桥易产生较大的振动和噪声，同时，瞬间产生的制动力矩作用在传动系中，会对变速箱齿轮、尤其是后桥齿轮产生较大冲击，加剧了后桥振动噪声，影响了后桥使用寿命；另一方面，在缓速器不制动时，车辆在高速滑行过程中，后桥齿轮拖动传动轴及缓速器转子，由于缓速器转子的转动惯量较大，使得后桥齿轮负载波动较大，易引起后桥振动及噪声，另外，在车辆启动及急加速过程中，缓速器转子会随发动机转速和扭矩的快速变化而产生加速度，由于缓速器转子转动惯量大和传动轴后桥等轴系装配间隙的存在，缓速器转子产生较大的扭转冲击力会直接传递到后桥齿轮系，使得后桥主减速器主背齿轮的瞬时接触力加大，进而产生较大的振动和噪声。
通过以上介绍可知，电涡流缓速器虽然提升了车辆的制动安全性能，但也对整车的舒适性带来了诸多负面的影响。因此，有必要对缓速器结构进行优化，增加相应的振动噪声控制措施。
发明内容
本发明的目的在于提供一种具有扭转减振功能的电涡流缓速器，以减小缓速器给车辆带来的振动和噪声。
为了解决上述问题，本发明的具有扭转减振功能的电涡流缓速器采用以下技术方案：具有扭转减振功能的电涡流缓速器，包括定子、用于与车辆变速箱连接的上游转子和用于与车辆后桥前端传动轴连接的下游转子，所述下游转子上设有用于与车辆后桥前端传动轴连接的减振缓冲装置。
所述减振缓冲装置包括与下游转子同轴设置的从动盘毂，所述从动盘毂与下游转子之间传动连接并且二者之间具有相对转动余量，下游转子与从动盘毂之间设有用于缓冲二者之间相对转动产生的冲击的弹性缓冲件。
所述从动盘毂与下游转子之间的转动余量由销与相应销孔间的间隙形成。
所述弹性缓冲件为顶在下游转子和从动盘毂之间的螺旋弹簧，螺旋弹簧的中心线与下游转子的中心线空间垂直交叉。
所述下游转子包括固设于一起的内盘和外盘，所述外盘和从动盘毂上设有互相对应的弹簧窗孔，所述螺旋弹簧设在外盘和从动盘毂的弹簧窗孔中，外盘和从动盘毂沿螺旋弹簧的径向共跨在螺旋弹簧上。
所述从动盘毂的外侧设有有弹簧卡盘，螺旋弹簧通过弹簧卡盘向外防脱的装配在相应的弹簧窗孔中。
所述从动盘毂与下游转子之间和/或与弹簧卡盘之间设有减振阻尼垫片。
所述从动盘毂与下游转子之间设有减振阻尼垫片。
所述下游转子为不产生制动力的非制动转子。
所述下游转子为不产生制动力的非制动转子。
在该电涡流缓速器中，由于下游转子上设有用于与车辆后桥前端传动轴连接的减振缓冲装置，因此，在工作时，瞬间产生的扭转反力矩作用于减振缓冲装置上，通过减振缓冲装置的缓冲及衰减作用，将瞬间产生的扭矩冲击减小，从而可达到减小冲击，减轻振动的目的，另外，在缓速器不制动时，减振缓冲装置串联在传动系统中，有利于衰减由发动机和轴系空间夹角产生的扭矩波动，提升传动系的NVH性能。综上所述，该电涡流缓速器能减小缓速器给车辆带来的振动和噪声。
更进一步的，从动盘毂是为了方便对弹性缓冲件的设置，同时作为接口输出动力；采用螺旋弹簧作为弹性缓冲件便于实现对弹性刚度的调节；减振阻尼垫片是为了通过减振盘毂与下游转子和弹簧卡盘之间的摩擦来消耗扭转振动能量使扭转振动迅速衰减；将下游转子设为不产生制动力的非制动转子是为了使减振缓冲装置一侧无热量产生，这有利于延长该缓速器及减振装置的使用寿命，同时减轻整体转子的转动惯量。
附图说明
图1是具有扭转减振功能的电涡流缓速器的实施例的主视图；
图2是具有扭转减振功能的电涡流缓速器的实施例的左视图；
图3是下游转子与减振缓冲装置的分解图。
具体实施方式
具有扭转减振功能的电涡流缓速器的实施例，如图1-3所示，该具有扭转减振功能的电涡流缓速器包括定子11、上游转子12和下游转子13，上游转子12用于与车辆变速箱连接，下游转子13用于与车辆后桥前端传动轴连接。另外，下游转子13上设有用于与车辆后桥前端传动轴连接的减振缓冲装置。
在本实施例中，下游转子13是由固设于一起的内盘131和外盘132构成，内、外盘之间具有一个间隙，二者之间是通过边缘处的一些连接筋连接在一起的，动力由上游转子12通过内盘131传递给外盘132。减振缓冲装置包括与下游转子13同轴设置的从动盘毂14，同轴度可由外盘132上内孔24及从动盘毂14内侧凸缘确定，外盘132与弹簧卡盘18通过铆钉孔21铆成一个整体，并将从动盘毂14及其两侧的阻尼片20夹在中间，铆钉通过从动盘毂14上的凹槽22，并与凹槽22两边留有一定的间隙余量，该间隙余量决定了动盘毂14与外盘132之间的相对转动角度，外盘132与动盘毂14之间采用弹性缓冲件连接传动，弹性缓冲件采用的是螺旋弹簧16(其它实施例中还可以为大弹簧与小弹簧并联形成的二级减振弹簧、弹性橡胶等)，螺旋弹簧16的中心线与下游转子13的中心线空间垂直交叉，为了实现对螺旋弹簧16的安装，下游转子13的外盘132和从动盘毂14上设有互相对应的弹簧窗孔17，螺旋弹簧16设在外盘132和从动盘毂14的弹簧窗孔中，其中外盘132和从动盘毂14共跨螺旋弹簧16径向上的半边，下游转子13的外盘螺栓窗孔上的翻边可以阻挡螺旋弹簧16从外盘内侧脱出，从动盘毂14与弹簧卡盘18共跨螺旋弹簧16径向上的另外半边，螺旋弹簧16通过弹簧卡盘18向外防脱的装配在相应的弹簧窗孔中，具体地说，弹簧卡盘18上开有与弹簧窗孔对应的开口，但是该开口处具有向外翻折的翻边19，翻边19以翻铆的方式将螺旋弹簧16限制在了相应的弹簧窗孔中，从而实现了螺旋弹簧16的向外防脱。
另外，在本实施例中，从动盘毂与下游转子之间和与弹簧卡盘之间分别还设有减振阻尼垫片20，减振阻尼垫片20是为了通过减振盘毂与下游转子和弹簧卡盘之间的摩擦来消耗扭转振动能量使扭转振动迅速衰减。
下游转子13为不产生制动力的非制动转子。这一点可通过改变定子线圈的缠绕方式 来实现，使之只在一端(上游转子端)产生磁力线，产生制动作用，另一端(下游转子端)无磁力线产生，即无制动作用。
本实施例中，动力由上游转子12传递给下游转子13，转子13通过螺旋弹簧16将减振后的动力传递给从动盘毂14，之后通过动盘毂14上的法兰接口23传递给后桥前端传动轴。

Claims (10)

  1. 具有扭转减振功能的电涡流缓速器，包括定子、用于与车辆变速箱连接的上游转子和用于与车辆后桥前端传动轴连接的下游转子，其特征在于，所述下游转子上设有用于与车辆后桥前端传动轴连接的减振缓冲装置。
  2. 根据权利要求1所述的具有扭转减振功能的电涡流缓速器，其特征在于，所述减振缓冲装置包括与下游转子同轴设置的从动盘毂，所述从动盘毂与下游转子之间传动连接并且二者之间具有相对转动余量，下游转子与从动盘毂之间设有用于缓冲二者之间相对转动产生的冲击的弹性缓冲件。
  3. 根据权利要求2所述的具有扭转减振功能的电涡流缓速器，其特征在于，所述从动盘毂与下游转子之间的转动余量由销与相应销孔间的间隙形成。
  4. 根据权利要求2所述的具有扭转减振功能的电涡流缓速器，其特征在于，所述弹性缓冲件为顶在下游转子和从动盘毂之间的螺旋弹簧，螺旋弹簧的中心线与下游转子的中心线空间垂直交叉。
  5. 根据权利要求4所述的具有扭转减振功能的电涡流缓速器，其特征在于，所述下游转子包括固设于一起的内盘和外盘，所述外盘和从动盘毂上设有互相对应的弹簧窗孔，所述螺旋弹簧设在外盘和从动盘毂的弹簧窗孔中，外盘和从动盘毂沿螺旋弹簧的径向共跨在螺旋弹簧上。
  6. 根据权利要求5所述的具有扭转减振功能的电涡流缓速器，其特征在于，所述从动盘毂的外侧设有有弹簧卡盘，螺旋弹簧通过弹簧卡盘向外防脱的装配在相应的弹簧窗孔中。
  7. 根据权利要求6所述的具有扭转减振功能的电涡流缓速器，其特征在于，所述从动盘毂与下游转子之间和/或与弹簧卡盘之间设有减振阻尼垫片。
  8. 根据权利要求1-5任一项所述的具有扭转减振功能的电涡流缓速器，其特征在于，所述从动盘毂与下游转子之间设有减振阻尼垫片。
  9. 根据权利要求8所述的具有扭转减振功能的电涡流缓速器，其特征在于，所述下游转子为不产生制动力的非制动转子。
  10. 根据权利要求1-7任一项所述的具有扭转减振功能的电涡流缓速器，其特征在于，所述下游转子为不产生制动力的非制动转子。
PCT/CN2014/092515 2013-12-06 2014-11-28 具有扭转减振功能的电涡流缓速器 WO2015081814A1 (zh)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201310649556.9 2013-12-06
CN201310649556.9A CN103692918B (zh) 2013-12-06 2013-12-06 具有扭转减振功能的电涡流缓速器

Publications (1)

Publication Number Publication Date
WO2015081814A1 true WO2015081814A1 (zh) 2015-06-11

Family

ID=50354648

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2014/092515 WO2015081814A1 (zh) 2013-12-06 2014-11-28 具有扭转减振功能的电涡流缓速器

Country Status (2)

Country Link
CN (1) CN103692918B (zh)
WO (1) WO2015081814A1 (zh)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016218711A1 (de) 2016-09-28 2018-03-29 Zf Friedrichshafen Ag Kraftfahrzeugantriebsstrang
CN109951148A (zh) * 2019-05-10 2019-06-28 浙江正泰新能源开发有限公司 光伏跟踪器传动装置
CN110027814A (zh) * 2019-04-03 2019-07-19 西安卓士博液压工程有限责任公司 一种减振法兰
CN111075886A (zh) * 2018-10-19 2020-04-28 郑州宇通客车股份有限公司 扭转减振器及使用该扭转减振器的车辆
CN115182937A (zh) * 2022-07-18 2022-10-14 西南石油大学 一种用于曲轴振动控制的变刚度叠片联轴器
CN111075886B (zh) * 2018-10-19 2024-05-31 宇通客车股份有限公司 扭转减振器及使用该扭转减振器的车辆

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103692918B (zh) * 2013-12-06 2015-12-30 郑州宇通客车股份有限公司 具有扭转减振功能的电涡流缓速器
WO2016123638A1 (en) * 2015-01-28 2016-08-04 Johannes Van Der Merwe Jacobus Efficient electric generator
CN106627091B (zh) * 2015-07-16 2019-07-19 上海汽车集团股份有限公司 混合动力汽车、电机驱动传动系统及其减振机构
CN107034622B (zh) * 2017-05-31 2020-10-02 青岛海尔智能技术研发有限公司 平衡环、用于平衡环的控制方法和洗衣机
CN108668604B (zh) * 2018-06-26 2023-07-07 中机美诺科技股份有限公司 青贮饲料收获机动力输出装置和青贮饲料收获机
DE102018115310A1 (de) * 2018-06-26 2020-01-02 Schaeffler Technologies AG & Co. KG Drehmomentübertragungsvorrichtung mit einem Steuerungssystem zur Ermittlung der Drehrichtung des Rotors
CN115076295A (zh) * 2022-06-17 2022-09-20 中国第一汽车股份有限公司 一种扭转减振器

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5513729A (en) * 1994-06-08 1996-05-07 Labavia Sge Vehicle transmissions equipped with eddy current retarders, and in fastener members for such transmissions
CN101764500A (zh) * 2010-01-12 2010-06-30 瑞立集团有限公司 一种电涡流缓速器
CN102050031A (zh) * 2010-11-22 2011-05-11 瑞立集团有限公司 一种电涡流缓速器的安装结构
CN103692918A (zh) * 2013-12-06 2014-04-02 郑州宇通客车股份有限公司 具有扭转减振功能的电涡流缓速器
CN203637589U (zh) * 2013-12-06 2014-06-11 郑州宇通客车股份有限公司 一种具有扭转减振功能的电涡流缓速器

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3955691B2 (ja) * 1999-02-10 2007-08-08 財団法人鉄道総合技術研究所 鉄道車両用渦電流減速装置
CN201808461U (zh) * 2010-01-12 2011-04-27 瑞立集团有限公司 汽车制动用电涡流缓速器及装有该电涡流缓速器的汽车
CN103368356A (zh) * 2012-03-27 2013-10-23 泰乐玛汽车制动系统（上海）有限公司 电涡流缓速器及使用该电涡流缓速器的交通设备

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5513729A (en) * 1994-06-08 1996-05-07 Labavia Sge Vehicle transmissions equipped with eddy current retarders, and in fastener members for such transmissions
CN101764500A (zh) * 2010-01-12 2010-06-30 瑞立集团有限公司 一种电涡流缓速器
CN102050031A (zh) * 2010-11-22 2011-05-11 瑞立集团有限公司 一种电涡流缓速器的安装结构
CN103692918A (zh) * 2013-12-06 2014-04-02 郑州宇通客车股份有限公司 具有扭转减振功能的电涡流缓速器
CN203637589U (zh) * 2013-12-06 2014-06-11 郑州宇通客车股份有限公司 一种具有扭转减振功能的电涡流缓速器

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016218711A1 (de) 2016-09-28 2018-03-29 Zf Friedrichshafen Ag Kraftfahrzeugantriebsstrang
CN111075886A (zh) * 2018-10-19 2020-04-28 郑州宇通客车股份有限公司 扭转减振器及使用该扭转减振器的车辆
CN111075886B (zh) * 2018-10-19 2024-05-31 宇通客车股份有限公司 扭转减振器及使用该扭转减振器的车辆
CN110027814A (zh) * 2019-04-03 2019-07-19 西安卓士博液压工程有限责任公司 一种减振法兰
CN110027814B (zh) * 2019-04-03 2024-01-26 西安卓士博液压工程有限责任公司 一种减振法兰
CN109951148A (zh) * 2019-05-10 2019-06-28 浙江正泰新能源开发有限公司 光伏跟踪器传动装置
CN109951148B (zh) * 2019-05-10 2024-02-09 浙江正泰新能源开发有限公司 光伏跟踪器传动装置
CN115182937A (zh) * 2022-07-18 2022-10-14 西南石油大学 一种用于曲轴振动控制的变刚度叠片联轴器
CN115182937B (zh) * 2022-07-18 2023-06-02 西南石油大学 一种用于曲轴振动控制的变刚度叠片联轴器

Also Published As

Publication number Publication date
CN103692918A (zh) 2014-04-02
CN103692918B (zh) 2015-12-30

Similar Documents

Publication Publication Date Title
WO2015081814A1 (zh) 具有扭转减振功能的电涡流缓速器
JP5394531B2 (ja) 電気自動車の動力伝達装置
EP2765331A2 (en) Power transmission apparatus
EP2765330A2 (en) Power transmission apparatus
WO2012137234A1 (ja) 捩り振動減衰装置
KR20170058945A (ko) 회전 진동 댐퍼를 갖는 클러치 디스크
US9091304B2 (en) Torsional vibration attenuation apparatus
CN103204059A (zh) 一种电动车轮边电驱动系统
JP5527428B2 (ja) 捩り振動減衰装置
CN109677210B (zh) 一种控制可断开半轴的驱动桥的方法
CN202518082U (zh) 电动车轮边电驱动装置
CN212028426U (zh) 车辆用减振器及车辆
CN203537208U (zh) 一种电涡流缓速器
CN203637589U (zh) 一种具有扭转减振功能的电涡流缓速器
CN109677209B (zh) 一种可断开半轴的驱动桥的控制方法
CN110576705B (zh) 一种车辆及驱动桥、半轴组件
CN206727750U (zh) 一种减振转子及使用该减振转子的电涡流缓速器和汽车
CN205937629U (zh) 新能源车型用缓冲盘结构
CN104578683A (zh) 一种电涡流缓速器
CN206790281U (zh) 金属橡胶复合弹簧发电机减振带轮
CN205190566U (zh) 一种汽车离合器盘结构
CN104565193A (zh) 一种扭转减振器
CN203766538U (zh) 缓速器装置及使用该缓速器装置的车辆
KR20050020905A (ko) 클러치 디스크
CN206668861U (zh) 一种用于电动汽车的减震传动轴

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 14867284

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 14867284

Country of ref document: EP

Kind code of ref document: A1