WO2019178745A1 - 扭转减振器 - Google Patents

扭转减振器 Download PDF

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Publication number
WO2019178745A1
WO2019178745A1 PCT/CN2018/079620 CN2018079620W WO2019178745A1 WO 2019178745 A1 WO2019178745 A1 WO 2019178745A1 CN 2018079620 W CN2018079620 W CN 2018079620W WO 2019178745 A1 WO2019178745 A1 WO 2019178745A1
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WO
WIPO (PCT)
Prior art keywords
support ring
torsional vibration
vibration damper
flange
ring
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Application number
PCT/CN2018/079620
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English (en)
French (fr)
Inventor
薛勇
Original Assignee
舍弗勒技术股份两合公司
薛勇
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 舍弗勒技术股份两合公司, 薛勇 filed Critical 舍弗勒技术股份两合公司
Priority to DE112018007303.3T priority Critical patent/DE112018007303T5/de
Priority to CN201880090272.1A priority patent/CN111771072B/zh
Priority to PCT/CN2018/079620 priority patent/WO2019178745A1/zh
Publication of WO2019178745A1 publication Critical patent/WO2019178745A1/zh

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12Suppression 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
    • F16F15/129Suppression 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
    • F16F15/1292Suppression 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 characterised by arrangements for axially clamping or positioning or otherwise influencing the frictional plates
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12Suppression 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
    • F16F15/121Suppression 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
    • F16F15/123Wound springs
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2230/00Purpose; Design features
    • F16F2230/0052Physically guiding or influencing
    • F16F2230/0064Physically guiding or influencing using a cam

Definitions

  • the present invention relates to components of a transmission system, and more particularly to a torsional vibration damper.
  • a torsional vibration damper is known from the prior art such as CN107429789A, CN107076260A.
  • a torsional vibration damper can in particular be a dual mass flywheel for damping torsional vibrations of the drive shaft of a motor vehicle engine.
  • FIG. 1 shows a partial cross-sectional view of a known torsional vibration damper 100.
  • the torsional vibration damper 100 includes a distance disc 10 for connection to a crankshaft, a primary mass (primary flywheel) 20, and a retaining ring 30.
  • the disc 10, the primary mass 20, and the retaining ring 30 are secured together by rivets 110.
  • the torsional vibration damper 100 further includes a flange 40, a secondary mass (hub) 50, and a diaphragm spring 60 located between the flange 40 and the secondary mass 50.
  • the flange 40, the secondary mass 50 and the diaphragm spring 60 are secured together by rivets 120.
  • the inner peripheral portion of the secondary mass 50 forms a spline sleeve 51 for outputting rotation to, for example, an input shaft of the transmission.
  • the torsional vibration damper 100 further includes a passage cover member 70 welded to the primary mass member 20 at the outer periphery, at a radially outer portion of the torsional vibration damper 100, defined between the primary mass member 20 and the passage cover member 70 for receiving A channel that acts as an arc spring for the energy storage element.
  • the torsional vibration damper 100 also includes a friction ring 80 that presses the friction ring 80 against the passage cover member 70. Since the contact surface of the friction ring 80 and the passage cover member 70 is large, the frictional force is also large, and therefore, during the rotation of the primary mass member 20 and the passage cover member 70 with respect to the flange 40 and the secondary mass member 50, Only the diaphragm spring 60 and the friction ring 80 rotate relative to each other, and the friction ring 80 and the passage cover member 70 maintain static friction and are relatively fixed.
  • the torsional vibration damper 100 also includes a support ring 90 for supporting the flange 40.
  • a support ring 90 for supporting the flange 40.
  • the radially extending portion of the support ring 90 is sandwiched between the primary mass 20 and the flange 40.
  • a torsional vibration damper includes a primary mass, a support ring, a flange, a diaphragm spring, a secondary mass, and a passage cover, the primary mass and the passage cover being secured together at an outer periphery In the axial direction of the torsional vibration damper, at least a portion of the support ring is disposed between the primary mass and the flange, the flange, the diaphragm spring and the secondary The mass members are secured together, the diaphragm spring being located between the flange and the secondary mass and resiliently pressed against the passage cover member,
  • the support ring includes an adjustment support ring and a fixed support ring supporting the flange
  • the adjustment support ring has a wedge-shaped axial section
  • the flange is plastically deformed and/or the diaphragm spring is plastically deformed such that the flange
  • the fixed support ring is a ring member having a generally L-shaped axial section
  • the adjustment support ring includes a plurality of arcuate ring segments.
  • the contact surface of the fixed support ring and the adjustment support ring assumes a straight line that is inclined with respect to the radial direction of the torsional vibration damper.
  • the axial thickness of the adjustment support ring is formed to be smaller toward the radially outer side of the torsional vibration damper.
  • the fixed support ring includes: an axially extending portion extending along an axial direction and a circumferential direction of the torsional vibration damper; and a radial and circumferential direction along the torsional vibration damper
  • the radially extending portion of the extension, the axial thickness of the radially extending portion is larger toward the radially outer side.
  • the adjustment support ring is disposed between the fixed support ring and the primary mass, the torsional vibration damper further comprising a retaining ring secured to the primary mass, The retaining ring is configured to prevent the ring segment of the adjustment support ring from falling toward the radially inner side of the torsional vibration damper.
  • the adjustment support ring is disposed between the fixed support ring and the flange, the fixed support ring preventing the diameter of the ring segment of the adjustment support ring from facing the torsional vibration damper Drop to the inside.
  • the adjustment support ring is made of plastic.
  • the torsional vibration damper further includes a friction ring through which the outer peripheral portion of the diaphragm spring is pressed against the passage cover.
  • the torsional vibration damper is a dual mass flywheel or a dual clutch damper.
  • the adjusting support ring can be moved radially outward by the centrifugal force, thereby maintaining or increasing the axial distance between the primary mass and the flange, ensuring the diaphragm spring
  • the spring force is approximately constant.
  • Figure 1 shows a partial axial cross-sectional view of a known torsional vibration damper.
  • FIG. 2A shows a partial cross-sectional view of a torsional vibration damper in accordance with a first embodiment of the present invention.
  • Fig. 2B shows a partial enlarged view of the torsional vibration damper of Fig. 2A.
  • Figure 3 shows an axial view of the torsional vibration damper of Figure 2A.
  • Figure 4 shows a partial cross-sectional view of the torsional vibration damper of Figure 2A after use.
  • Figure 5 shows an axial view of the torsional vibration damper of Figure 2A after use.
  • FIGS. 6A and 6B show partial cross-sectional views of a torsional vibration damper according to a second embodiment of the present invention.
  • a first embodiment of the present invention provides a torsional vibration damper 200.
  • the partial structure of the torsional vibration damper 200 is the same as that of the torsional vibration damper 200 of FIG. Therefore, the same or similar reference numerals are given to the same or like components as those in FIG. 1, and the improvement of the structure of FIG. 1 by the present invention will be mainly described below.
  • the existing single support ring 90 is divided into two members, a fixed support ring 91 and an adjustment support ring 92.
  • the fixed support ring 91 and the adjustment support ring 92 are relatively movable.
  • the fixed support ring 91 is in contact with the flange 40 for supporting the flange 40. More specifically, the fixed support ring 91 includes: an axially extending portion 91A for extending in contact with the inner circumference of the flange 40 substantially along the axial direction A and the circumferential direction C of the torsional vibration damper 200; and extending axially
  • the portion 91A is integrally formed with a radially extending portion 91B extending substantially along the radial direction R and the circumferential direction C of the torsional vibration damper 200.
  • the radially extending portion 91B is located between the adjustment support ring 92 and the flange 40, and the axial one side of the radially extending portion 91B (the right side of FIGS.
  • the other axial side 911 (see FIG. 2B) is in contact with the adjustment support ring 92.
  • the axially extending portion of the radially extending portion 91B is substantially wedge-shaped, and the axial thickness of the radially extending portion 91B is formed to be larger toward the radially outer side. More specifically, in the axial section of the torsional vibration damper 200, the other side surface 911 is formed as a diagonal line inclined with respect to the radial direction R.
  • the adjustment support ring 92 is located between the primary mass 20 and the stationary support ring 91.
  • the axial section of the adjustment support ring 92 is also substantially wedge-shaped, and the axial thickness of the adjustment support ring 92 is formed to be smaller toward the radially outer side. More specifically, in the axial section of the torsional vibration damper 200, the axial one side surface 921 of the adjustment support ring 92 is formed as a diagonal line inclined with respect to the radial direction R.
  • the distance disk 10, the primary mass 20, and the like are omitted in Figures 3 and 5 such that the fixed support ring 91 and the adjustment support ring 92 are axially visible.
  • the fixed support ring 91 is preferably formed as a single piece, and the adjustment support ring 92 is divided into a plurality of ring segments 92A, 92B, 92C each having an arc shape. 92D.
  • Dividing the support ring 92 into a plurality of ring segments 92A, 92B, 92C, 92D ensures that the adjustment support ring 92 can move radially outward relative to the fixed support ring 91, particularly if the support ring 90 is worn.
  • the retaining ring 30 can support a plurality of ring segments 92A, 92B, 92C, 92D from a radially inner side to prevent adjustment of one or more ring segments 92A, 92B, 92C of the support ring 92,
  • the 92D drops or disengages from the desired position, particularly when assembling the torsional vibration damper 200.
  • the adjustment support ring 92 in the new state (the state in which the torsional vibration damper 200 is initially used), the adjustment support ring 92 can be held in its mounted position to maintain the centrifugal force and the spring of the diaphragm spring 60 due to the centrifugal force of the adjustment support ring 92. The effect of the force is balanced.
  • the pressure exerted by the diaphragm spring 60 on the support ring 90 via the flange 40 is reduced due to wear of the support ring 90 and/or plastic deformation of the diaphragm spring 60.
  • the adjustment support ring 92 under the action of the centrifugal force, the adjustment support ring 92 is moved outward in the radial direction, thereby keeping the spring force of the diaphragm spring 60 substantially constant.
  • the adjustment support ring 92 is preferably made of a flexible material such as plastic.
  • the ring segments 92A, 92B, 92C, 92D can be slightly curved to better match the shape of the fixed support ring 91.
  • adjustment support ring 92 and the radially extending portion 91B of the fixed support ring 91 are sized to adjust the support ring 92 from being radially outwardly disengaged from the fixed support ring 91 by centrifugal force.
  • Movement of the adjustment support ring 92 relative to the fixed support ring 91 can maintain the distance between the primary mass 20 and the flange 40 substantially constant as the support ring 90 wears.
  • the diaphragm spring 60 is plastically deformed to cause its spring force to decrease, the movement of the adjustment support ring 92 relative to the fixed support ring 91 can increase the axial distance between the primary mass member 20 and the flange 40, thereby maintaining the diaphragm spring.
  • the spring force of 60 is substantially constant.
  • the torsional vibration damper 200 of the present embodiment can keep the base damping constant, thereby extending the life of the torsional vibration damper 200.
  • torsional vibration damper 200 of the present embodiment can be used as a dual mass flywheel or a dual clutch damper.
  • FIGS. 6A and 6B illustrate a torsional vibration damper 300 in accordance with a second embodiment of the present invention, wherein for the sake of simplicity, only the structure around the support ring 90 is shown.
  • the same or similar reference numerals are given to the same or like components as those of the first embodiment, and a detailed description of these components will be omitted.
  • the fixed support ring 91 for supporting the flange 40 is in contact with the primary mass member 20. More specifically, the fixed support ring 91 includes: an axially extending portion 91A extending substantially in the axial direction A and the circumferential direction C of the torsional vibration damper 300 in contact with the inner peripheral edge of the flange 40; and extending axially
  • the portion 91A is integrally formed with a radially extending portion 91B extending substantially along the radial direction R and the circumferential direction C.
  • the radially extending portion 91B is located between the primary mass member 20 and the adjustment support ring 92.
  • the axially extending portion of the radially extending portion 91B is substantially wedge-shaped, and the axial thickness of the radially extending portion 91B is formed to be larger toward the radially outer side.
  • the axial one side surface 912 of the radially extending portion 91B is formed as a diagonal line inclined with respect to the radial direction R.
  • the adjustment support ring 92 is located between the fixed support ring 91 and the flange 40.
  • the axial section of the adjustment support ring 92 is also substantially wedge-shaped, and the axial thickness of the adjustment support ring 92 is formed to be smaller toward the radially outer side. More specifically, in the axial section of the torsional vibration damper 300, the other axial side surface 922 of the adjustment support ring 92 is formed as a diagonal line inclined with respect to the radial direction R.
  • This embodiment can operate similarly to the first embodiment.
  • the adjustment support ring 92 can be moved radially outward by the centrifugal force, thereby maintaining or increasing the primary mass member 20.
  • the axial distance between the flange 40 and the flange 40 ensures that the spring force of the diaphragm spring 60 is substantially constant.
  • the axially extending portion 91A of the fixed support ring 91 can function as a ring segment that prevents the adjustment of the support ring 92 (refer to FIGS. 3 and 5), particularly when assembling the torsional vibration damper 300 toward the radially inner side. Dropped.
  • the retaining ring 30 is not required to support the adjustment support ring 92.
  • the adjustment support ring 92 is divided into four ring segments 92A, 92B, 92C, 92D, however, the present invention is not limited thereto, and for example, the adjustment support ring 92 may be divided into two or three. Or other number of ring segments.
  • the outer peripheral portion of the diaphragm spring 60 is elastically pressed against the passage cover member 70 by the friction ring 80.
  • the invention is not limited thereto.
  • the friction ring 80 can be omitted and the diaphragm spring 60 can be directly elastically pressed against the passage cover member 70.
  • the axial section of the adjustment support ring 92 and the fixed support ring 91 is not limited to the illustrated shape as long as the adjustment support ring 92 can be subjected to centrifugal force in the case of component wear and/or plastic deformation of the diaphragm spring 60. It is possible to move toward the radially outer side with respect to the fixed support ring 91 to maintain the spring force of the diaphragm spring 60 substantially constant.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

一种扭转减振器(100,200,300),其中,初级质量件(20)和通道盖件(70)在外周缘固定到一起,在扭转减振器(100,200,300)的轴向上,支承环(90)的至少一部分设置在初级质量件(20)和法兰(40)之间,法兰(40)、膜片弹簧(60)和次级质量件(50)固定到一起,膜片弹簧(60)位于法兰(40)和次级质量件(50)之间并与通道盖件(70)弹性压抵。其中,支承环(90)包括调节支承环(92)和支承法兰(40)的固定支承环(91),调节支承环(92)的轴向截面为楔形,在磨损和/或膜片弹簧(60)塑性变形使得法兰(40)和初级质量件(20)之间的压力变小时,调节支承环(92)在离心力的作用下相对于固定支承环(91)朝向扭转减振器(100,200,300)的径向外侧移动,从而保持或增大初级质量件(20)和法兰(40)之间的轴向距离,维持膜片弹簧(60)的弹簧力大致恒定。

Description

扭转减振器 技术领域
本发明涉及传动系统的部件,更具体地涉及一种扭转减振器。
背景技术
目前,已有各种减振器用于改善机动车的NVH性能。例如,从CN107429789A、CN107076260A等现有技术中已知扭转减振器。这种扭转减振器特别地可以是双质量飞轮,用于减弱机动车发动机的驱动轴的扭转振动。
为了减小扭转减振器的共振,需要使基础阻尼保持为适当值。
图1示出了一种已知的扭转减振器100的局部剖视图。该扭转减振器100包括用于连接到曲轴的距离盘10、初级质量件(初级飞轮)20、保持环30。距离盘10、初级质量件20、保持环30通过铆钉110固定到一起。
扭转减振器100还包括法兰40、次级质量件(轮毂)50和位于法兰40、次级质量件50之间的膜片弹簧60。法兰40、次级质量件50和膜片弹簧60通过铆钉120固定到一起。次级质量件50的内周部分形成花键套51,用于将转动输出到例如变速器的输入轴。
扭转减振器100还包括在外周缘焊接到初级质量件20的通道盖件70,在扭转减振器100的径向外侧部分,在初级质量件20和通道盖件70之间限定用于容纳作为储能元件的弧形弹簧的通道。
扭转减振器100还包括摩擦环80,膜片弹簧60将摩擦环80压在通道盖件70上。由于摩擦环80与通道盖件70的接触面较大,摩擦力也较大,因此,在初级质量件20和通道盖件70相对于法兰40和次级质量件50旋转的过程中,可看作只有膜片弹簧60和摩擦环80之间有相对转动,摩擦环80与通道盖件70保持静摩擦,相对固定。
扭转减振器100还包括用于支承法兰40的支承环90。在扭转减振器100的轴向A上,支承环90的径向延伸部分被夹在初级质量件20和法兰40之间。因此,在支承环90与初级质量件20和/或法兰40之间存在转动摩擦。
通过台架试验和路试发现,试验(使用)后的扭转减振器100的基础阻尼明显小于新(未使用的)扭转减振器100的基础阻尼。这主要是因为膜片弹簧60的弹簧力变小。弹簧力变小的原因是:(1)支承环90的磨损;以及(2)膜片弹簧60的塑性变形。对于图1所示的设计,没有部件能够补偿该磨损。
发明内容
本发明的目的在于克服或至少减轻上述现有技术存在的不足,提供一种可以在磨损和/或膜片弹簧塑性变形时自动调节膜片弹簧的弹簧力的扭转减振器。
提供一种扭转减振器,其包括初级质量件、支承环、法兰、膜片弹簧、次级质量件和通道盖件,所述初级质量件和所述通道盖件在外周缘固定到一起,在所述扭转减振器的轴向上,所述支承环的至少一部分设置在所述初级质量件和所述法兰之间,所述法兰、所述膜片弹簧和所述次级质量件固定到一起,所述膜片弹簧位于所述法兰和所述次级质量件之间并与所述通道盖件弹性压抵,
其中,所述支承环包括调节支承环和支承所述法兰的固定支承环,所述调节支承环的轴向截面为楔形,在磨损和/或所述膜片弹簧塑性变形使得所述法兰和所述初级质量件之间的压力变小时,所述调节支承环在离心力的作用下相对于所述固定支承环朝向所述扭转减振器的径向外侧移动,从而维持所述膜片弹簧的弹簧力大致恒定。
在至少一个实施方式中,所述固定支承环为轴向截面为大致L形的环构件,所述调节支承环包括多个弧形的环段。
在至少一个实施方式中,在所述支承环的轴向截面中,所述固定支承环和所述调节支承环的接触面呈现为相对于所述扭转减振器的径向倾斜的直线。
在至少一个实施方式中,所述调节支承环的轴向厚度形成为越向所述扭转减振器的径向外侧越小。
在至少一个实施方式中,所述固定支承环包括:沿着所述扭转减振器的轴向和周向延伸的轴向延伸部分;和沿着所述扭转减振器的径向和周向延伸的径向延伸部分,所述径向延伸部分的轴向厚度越向径向外侧越大。
在至少一个实施方式中,所述调节支承环设置在所述固定支承环和所述初级质量件之间,所述扭转减振器还包括与所述初级质量件固定在一起的保持环,所述保持环被构造成能够防止所述调节支承环的环段朝向所述扭转减振器的径向内侧掉落。
在至少一个实施方式中,所述调节支承环设置在所述固定支承环和所述法兰之间,所述固定支承环防止所述调节支承环的环段朝向所述扭转减振器的径向内侧掉落。
在至少一个实施方式中,所述调节支承环由塑料制成。
在至少一个实施方式中,所述扭转减振器还包括摩擦环,所述膜片弹簧的外周部通过所述摩擦环压抵所述通道盖件。
在至少一个实施方式中,所述扭转减振器为双质量飞轮或双离合器减振器。
在部件磨损和/或膜片弹簧塑性变形时,调节支承环可以在离心力的作用下朝向径向外侧移动,从而保持或增大初级质量件和法兰之间的轴向距离,确保膜片弹簧的弹簧力大致恒定。
附图说明
图1示出了一种已知的扭转减振器的局部轴向剖视图。
图2A示出了根据本发明的第一实施方式的扭转减振器的局部剖视图。
图2B示出了图2A中的扭转减振器的局部放大图。
图3示出了图2A中的扭转减振器的轴向视图。
图4示出了使用之后的图2A中的扭转减振器的局部剖视图。
图5示出了使用之后的图2A中的扭转减振器的轴向视图。
图6A和图6B示出了根据本发明的第二实施方式的扭转减振器的局部剖视图。
附图标记说明
100、200、300扭转减振器;10距离盘;20初级质量件;30保持环;40法兰;50次级质量件;51花键套;60膜片弹簧;70通道盖件;80摩擦环;90支承环;91固定支承环;91A轴向延伸部分;91B径向延伸部分;911径向延伸部分的轴向另一侧面;912径向延伸部分的轴向一侧面;92调节支承环;92A、92B、92C、92D环段;921调节支承环的轴向一侧面;922调节支承环的轴向另一侧面;110、120铆钉;
A轴向;R径向;C周向。
具体实施方式
下面参照附图描述本发明的示例性实施方式。
第一实施方式
参照图2A至图5,本发明的第一实施方式提供一种扭转减振器200。该扭转减振器200的部分结构与图1中的扭转减振器200的对应结构相同。因此,对于与图1中的部件相同或相似的部件标注了相同或相似的附图标记,下面主要说明本发明对图1的结构的改进之处。
在本实施方式中,将现有的单个支承环90分成了两个构件,即固定支承 环91和调节支承环92。固定支承环91和调节支承环92可以相对移动。
固定支承环91与法兰40接触,用于支承法兰40。更具体地,固定支承环91包括:用于与法兰40的内周缘接触的大致沿着扭转减振器200的轴向A和周向C延伸的轴向延伸部分91A;以及与轴向延伸部分91A一体形成的大致沿着扭转减振器200的径向R和周向C延伸的径向延伸部分91B。径向延伸部分91B位于调节支承环92和法兰40之间,径向延伸部分91B的轴向一侧面(图2A和图2B的右侧面)与法兰40的接触,径向延伸部分91B的轴向另一侧面911(参照图2B)与调节支承环92接触。径向延伸部分91B的轴向截面为大致楔形,径向延伸部分91B的轴向厚度形成为越向径向外侧越大。更具体地,在扭转减振器200的轴向截面中,另一侧面911形成为相对于径向R倾斜的斜线。
调节支承环92位于初级质量件20和固定支承环91之间。与固定支承环91的径向延伸部分91B对应地,调节支承环92的轴向截面也为大致楔形,调节支承环92的轴向厚度形成为越向径向外侧越小。更具体地,在扭转减振器200的轴向截面中,调节支承环92的轴向一侧面921形成为相对于径向R倾斜的斜线。
可以理解,在图3和图5中省略了距离盘10、初级质量件20等而使得固定支承环91和调节支承环92轴向可见。参照图3和图5,在扭转减振器200的周向C上,固定支承环91优选地形成为单件,调节支承环92分成均呈圆弧状的多个环段92A、92B、92C、92D。调节支承环92分成多个环段92A、92B、92C、92D确保了调节支承环92可以相对于固定支承环91朝向径向外侧移动,特别是在支承环90磨损的情况下。
参照图2A、图2B和图4,保持环30可以从径向内侧支撑多个环段92A、92B、92C、92D,从而防止调节支承环92的一个或多个环段92A、92B、92C、92D特别是在组装扭转减振器200时掉落或者脱离期望位置。
参照图2A至图3,在新状态(扭转减振器200被初始使用的状态),由于调节支承环92的离心力,调节支承环92能够保持在其安装位置使离心力和膜 片弹簧60的弹簧力的作用效果平衡。参照图4和图5,在使用后状态,由于支承环90的磨损和/或膜片弹簧60的塑性变形,膜片弹簧60的经由法兰40对支承环90施加的压力减小。此时,在离心力的作用下,调节支承环92将朝向径向外侧移动,从而保持膜片弹簧60的弹簧力大致恒定。
在本实施方式中,调节支承环92优选由塑料等挠性材料制成。这样,在调节支承环92向径向外侧移动时,环段92A、92B、92C、92D可以略微弯曲以更好地匹配固定支承环91的形状。
可以理解,调节支承环92和固定支承环91的径向延伸部分91B的尺寸被形成为调节支承环92不会由于离心力而向径向外侧移动到与固定支承环91脱离。
在支承环90磨损时,调节支承环92相对于固定支承环91的移动能够保持初级质量件20与法兰40之间的距离保持基本恒定。在膜片弹簧60塑性变形而导致其弹簧力减小时,调节支承环92相对于固定支承环91的移动能够增大初级质量件20与法兰40之间的轴向距离,从而保持膜片弹簧60的弹簧力大致恒定。因而,本实施方式的扭转减振器200可以保持基础阻尼恒定,从而延长扭转减振器200的寿命。
可以理解,本实施方式的扭转减振器200可以用作双质量飞轮或双离合器减振器。
第二实施方式
图6A和图6B示出了根据本发明的第二实施方式的扭转减振器300,其中,为了简单起见,仅示出了支承环90周围的结构。对于与第一实施方式相同或相似的部件标注相同或相似的附图标记,并省略对这些部件的详细说明。
在本实施方式中,用于支承法兰40的固定支承环91与初级质量件20接触。更具体地,固定支承环91包括:用于与法兰40的内周缘接触的大致沿着扭转减振器300的轴向A和周向C延伸的轴向延伸部分91A;以及与轴向延伸 部分91A一体形成的大致沿着径向R和周向C延伸的径向延伸部分91B。径向延伸部分91B位于初级质量件20和调节支承环92之间。径向延伸部分91B的轴向截面为大致楔形,径向延伸部分91B的轴向厚度形成为越向径向外侧越大。在扭转减振器300的轴向截面中,径向延伸部分91B的轴向一侧面912形成为相对于径向R倾斜的斜线。
调节支承环92位于固定支承环91和法兰40之间。与固定支承环91的径向延伸部分91B对应地,调节支承环92的轴向截面也为大致楔形,调节支承环92的轴向厚度形成为越向径向外侧越小。更具体地,在扭转减振器300的轴向截面中,调节支承环92的轴向另一侧面922形成为相对于径向R倾斜的斜线。
本实施方式可以与第一实施方式类似地动作。参照图6B,在第二实施方式中,在部件磨损和/或膜片弹簧60塑性变形时,调节支承环92可以在离心力的作用下朝向径向外侧移动,从而保持或增大初级质量件20和法兰40之间的轴向距离,确保膜片弹簧60的弹簧力大致恒定。
在第二实施方式中,固定支承环91的轴向延伸部分91A可以起到防止调节支承环92的环段(参照图3和图5)特别是在组装扭转减振器300时朝向径向内侧掉落。在本实施方式中,不需要保持环30来支撑调节支承环92。
当然,本发明不限于上述实施方式,本领域技术人员在本发明的教导下可以对本发明的上述实施方式做出各种变型,而不脱离本发明的范围。
(1)在第一实施方式中,调节支承环92被分成四个环段92A、92B、92C、92D,然而,本发明不限于此,例如,调节支承环92可以被分成两个、三个或其它数量的环段。
(2)在第一实施方式中,膜片弹簧60的外周部通过摩擦环80弹性压抵通道盖件70。然而,本发明不限于此。例如,可以省略摩擦环80而使膜片弹簧60直接弹性压抵通道盖件70。
(3)可以理解,调节支承环92和固定支承环91的轴向截面不限于图示 的形状,只要调节支承环92可以在部件磨损和/或膜片弹簧60塑性变形的情况下在离心力的作用下相对于固定支承环91朝向径向外侧移动从而保持膜片弹簧60的弹簧力大致恒定即可。

Claims (10)

  1. 一种扭转减振器,其包括初级质量件、支承环、法兰、膜片弹簧、次级质量件和通道盖件,所述初级质量件和所述通道盖件在外周缘固定到一起,在所述扭转减振器的轴向上,所述支承环的至少一部分设置在所述初级质量件和所述法兰之间,所述法兰、所述膜片弹簧和所述次级质量件固定到一起,所述膜片弹簧位于所述法兰和所述次级质量件之间并与所述通道盖件弹性压抵,
    其中,所述支承环包括调节支承环和支承所述法兰的固定支承环,所述调节支承环的轴向截面为楔形,在磨损和/或所述膜片弹簧塑性变形使得所述法兰和所述初级质量件之间的压力变小时,所述调节支承环在离心力的作用下相对于所述固定支承环朝向所述扭转减振器的径向外侧移动,从而维持所述膜片弹簧的弹簧力大致恒定。
  2. 根据权利要求1所述的扭转减振器,其特征在于,所述固定支承环为轴向截面为大致L形的环构件,所述调节支承环包括多个弧形的环段。
  3. 根据权利要求1所述的扭转减振器,其特征在于,在所述支承环的轴向截面中,所述固定支承环和所述调节支承环的接触面呈现为相对于所述扭转减振器的径向倾斜的直线。
  4. 根据权利要求1所述的扭转减振器,其特征在于,所述调节支承环的轴向厚度形成为越向所述扭转减振器的径向外侧越小。
  5. 根据权利要求1所述的扭转减振器,其特征在于,所述固定支承环包括:沿着所述扭转减振器的轴向和周向延伸的轴向延伸部分;和沿着所述扭转减振器的径向和周向延伸的径向延伸部分,所述径向延伸部分的轴向厚度越向径向外侧越大。
  6. 根据权利要求2所述的扭转减振器,其特征在于,所述调节支承环设置在所述固定支承环和所述初级质量件之间,所述扭转减振器还包括与所述 初级质量件固定在一起的保持环,所述保持环被构造成能够防止所述调节支承环的环段朝向所述扭转减振器的径向内侧掉落。
  7. 根据权利要求2所述的扭转减振器,其特征在于,所述调节支承环设置在所述固定支承环和所述法兰之间,所述固定支承环防止所述调节支承环的环段朝向所述扭转减振器的径向内侧掉落。
  8. 根据权利要求1至7中任一项所述的扭转减振器,其特征在于,所述调节支承环由塑料制成。
  9. 根据权利要求1至7中任一项所述的扭转减振器,其特征在于,所述扭转减振器还包括摩擦环,所述膜片弹簧的外周部通过所述摩擦环压抵所述通道盖件。
  10. 根据权利要求1至7中任一项所述的扭转减振器,其特征在于,所述扭转减振器为双质量飞轮或双离合器减振器。
PCT/CN2018/079620 2018-03-20 2018-03-20 扭转减振器 WO2019178745A1 (zh)

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