WO2022143636A1 - 摆动式减振装置和包括其的机动车辆 - Google Patents

摆动式减振装置和包括其的机动车辆 Download PDF

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Publication number
WO2022143636A1
WO2022143636A1 PCT/CN2021/141989 CN2021141989W WO2022143636A1 WO 2022143636 A1 WO2022143636 A1 WO 2022143636A1 CN 2021141989 W CN2021141989 W CN 2021141989W WO 2022143636 A1 WO2022143636 A1 WO 2022143636A1
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WO
WIPO (PCT)
Prior art keywords
swing
vibration damping
damping device
block
oscillating vibration
Prior art date
Application number
PCT/CN2021/141989
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English (en)
French (fr)
Inventor
王盛璋
张金鹏
孟腾
李璐
Original Assignee
法雷奥凯佩科液力变矩器(南京)有限公司
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Application filed by 法雷奥凯佩科液力变矩器(南京)有限公司 filed Critical 法雷奥凯佩科液力变矩器(南京)有限公司
Publication of WO2022143636A1 publication Critical patent/WO2022143636A1/zh

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    • 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
    • F16F15/131—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 the rotating system comprising two or more gyratory masses
    • 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
    • F16F15/131—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 the rotating system comprising two or more gyratory masses
    • F16F15/13142—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 the rotating system comprising two or more gyratory masses characterised by the method of assembly, production or treatment
    • F16F15/1315—Multi-part primary or secondary masses, e.g. assembled from pieces of sheet steel
    • 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
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers

Definitions

  • the present disclosure relates to a swing type vibration damping device.
  • the present disclosure also relates to torque converters, clutch discs, dual mass flywheels or motor vehicles including the oscillating damping device.
  • the torque produced by motor vehicle engines is often not constant. This non-constant torque can be transmitted into the transmission gearbox, causing vibrations in the transmission gearbox, and thus producing particularly undesirable noise or bumps or the like.
  • Torsional vibration damping devices allow the vibrations generated by the car engine to be absorbed and dampened.
  • a known torsional vibration damping device is an oscillating vibration damping device, which has a support which can be pivoted about an axis of rotation, and a wobble mass arranged on the support.
  • the oscillating block can swing relative to the support member around the rotation axis within a certain range, so as to absorb and reduce the vibration generated by the automobile engine through the inertial action of the oscillating block.
  • a rolling element is arranged between the support member and the swing block which is in rolling contact with both at the same time.
  • the oscillating mass is supported radially on the rolling elements, which themselves are supported radially on the bearing elements.
  • the swinging blocks are usually arranged in pairs, and the paired swinging blocks are usually connected together by rivets, and the support members are clamped therebetween, so that the swinging blocks can be restrained in the axial direction without hindering the swinging blocks relative to the supporting members. Oscillation of the axis of rotation.
  • the swing type vibration damping device usually includes a plurality of pairs of swing blocks arranged in a circumferential direction, and thus it is necessary to provide a plurality of rivets to connect the swing blocks.
  • the oscillating vibration damping device usually needs to use relatively expensive special rivets, which significantly increases the cost of the oscillating vibration damping device.
  • the additional riveting operation for connecting the swing blocks also increases the steps of assembling the swing type vibration damping device and increases the production cost.
  • the present disclosure aims to solve the above-mentioned problems in the conventional oscillating vibration damping device, and aims to provide a oscillating vibration damping device in which the oscillating blocks of the oscillating vibration damping device do not need to be connected by rivets.
  • the oscillating vibration damping device can reduce the complexity of components, reduce the number of components, facilitate manufacture and reduce costs.
  • the object is achieved by a swing type vibration damping device according to an embodiment of the present disclosure.
  • the oscillating vibration damping device includes: a support plate rotatable about an axis; at least one swing assembly movable relative to the support plate, the swing assembly including respectively arranged on axially opposite sides of the support plate. a first swing block and a second swing block, and a partition arranged between the first swing block and the second swing block and connecting the first swing block and the second swing block; at least one rolling member, the rolling member being clamped is held between a first rolling track defined by the support disc and a second rolling track defined by the spacer.
  • One of the first swing block and the second swing block is provided with a first connection groove, and the other of the first swing block and the second swing block is provided with a first connection protrusion, and the first connection protrusion has an interference fit.
  • the first connecting groove is inserted into the first connecting groove in a matched manner to connect the first swinging block and the second swinging block together.
  • the two swing blocks of the swing assembly of the swing type vibration damping device according to the present disclosure are connected by the connection protrusion and the connection groove of the interference fit, thereby eliminating the need for rivets for riveting. Therefore, the swing type vibration damping device according to the present disclosure can reduce the complexity of components, reduce the number of components, and reduce the cost of components. Meanwhile, by eliminating the riveting step, the assembly of the swing type vibration damping device according to the present disclosure is also simplified, and the production cost is reduced.
  • the oscillating vibration damping device may also have one or more of the following features, alone or in combination.
  • the support plate is provided with an anti-drop surface on its outer circumference that cooperates with the first connecting protrusion. Accordingly, when the engine of the motor vehicle is started and stopped, the first connecting protrusion can be supported on the anti-fall surface, thereby preventing the swing assembly from falling, thereby reducing noise between the partition and the rolling element, and the partition and the noise between the supports.
  • the predetermined threshold value is less than the minimum rotational speed after the engine is started. That is to say, when the engine of the motor vehicle is started, the swing assembly moves radially outward under the action of centrifugal force, so that the anti-fall surface is out of contact with the first connecting protrusion, thereby eliminating the noise generated by the friction between the two, And avoid friction damage to the support plate and swing assembly.
  • the first connecting protrusion follows the contour of the anti-fall surface when the rolling member moves along the first rolling track.
  • the minimum gap range between the first connecting protrusion and the anti-fall surface is constant when the rolling member moves along the first rolling track. That is to say, when the swing assembly swings relative to the support plate, the motion track followed by the first connecting protrusion matches the contour of the anti-drop surface, so that the distance between the first connecting protrusion and the anti-drop surface is at a constant minimum gap within the range.
  • the support plate is provided with stop surfaces at both ends of the anti-fall surface. Accordingly, when the swing assembly of the swing type vibration damping device reaches its maximum displacement, the first connecting protrusion contacts the stop surface to limit the relative movement range between the swing assembly and the support plate.
  • the support plate is provided with a radially outwardly concave inner recess on its inner circumference
  • the partition is located in the inner recess
  • the first rolling track is formed by The bottom surface of the inner recess is defined.
  • the inner recess cooperates with the partition to limit the relative movement range between the swing assembly and the support plate. That is, when the swing assembly of the swing-type vibration damping device reaches its maximum displacement, the side surface of the inner recess contacts with the partition, thereby limiting the relative movement range between the swing assembly and the support plate.
  • both the first swing block and the second swing block are provided with two stop holes, and the stop holes on the first swing block and the second swing block are opposite to each other standard for inserting two stops that constrain the position of the divider in the swing assembly.
  • At least one of the first swing block and the second swing block is further provided with a punched rivet
  • the partition is provided with a rivet hole aligned with the punched rivet.
  • both the first swing block and the second swing block are provided with punched rivets
  • the spacer is provided with two rivet holes, which are respectively aligned with the punched rivets of the first swing block and the second swing block. Accordingly, the first rocking mass and/or the second rocking mass partition can be connected with the partition.
  • the at least one swinging block is further provided with a punching boss, and the punching rivet is located on the punching boss.
  • the punched bosses and punched rivets are formed in different punching steps.
  • the at least one swinging block is punched to form a punched boss first, and then the punched boss is punched to form a punched rivet. By first forming the punching boss, a flat surface can be obtained, which is beneficial to control the orientation of the punching rivet.
  • the spacer is provided with a countersunk recess in which the rivet hole is arranged. Accordingly, after the riveting of the punched rivet to the rivet hole is completed, the rivet head will not protrude beyond the countersunk head recess, so that the connection between the two swing blocks will not be affected.
  • At least another one of the first swing block and the second swing block is further provided with a punched groove, and the punched groove, the rivet hole and the punched rivet are mutually Align.
  • At least one of the first swing block and the second swing block is further provided with a second connection groove, and the spacer is provided with an interference fit to be inserted into the the second connecting protrusion of the second connecting groove.
  • at least one of the first swing block and the second swing block is further provided with a second connection protrusion, and the second connection protrusion is inserted into the spacer provided on the partition in an interference fit manner. the second connection slot.
  • At least one of the first swing block and the second swing block has, on its side axially facing the support plate, a separation boss protruding from the side. According to this, the side surfaces of the swing block and the support disk only come into contact at the partition bosses, thereby avoiding large-area contact between the swing block and the support disk.
  • the first connecting protrusion has a chamfer on the end.
  • the second connecting protrusion also has a chamfer on the end. The chamfer can guide the interference fit between the connecting protrusion and the connecting groove, and can also accommodate burrs on the connecting protrusion and the connecting groove.
  • At least one of the support plate, the first rocking block, the second rocking block and the partition is manufactured by stamping.
  • the supporting plate, the first rocking block, the second rocking block and the partition are all manufactured by stamping.
  • At least one of the support plate, the first rocking block, the second rocking block and the partition is manufactured by stamping.
  • the present disclosure also provides a torque converter including the above-described swing type vibration damping device.
  • the present disclosure also provides a dual-mass flywheel including the swing-type vibration damping device as described above.
  • the present disclosure also provides a clutch disc including the oscillating vibration damping device as described above.
  • the present disclosure also provides a motor vehicle including at least one of the swing type vibration damping device, the torque converter, the dual mass flywheel and the clutch disc as described above.
  • FIG. 1 is a perspective view of a swing-type vibration damping device according to one embodiment of the present disclosure
  • Fig. 2 is an exploded view of the oscillating vibration damping device shown in Fig. 1;
  • 3A and 3B are enlarged views of a portion of the swing-type vibration damping device shown in FIG. 1;
  • Figure 4 shows the support plate of the oscillating vibration damping device
  • Figures 5A and 5B show two embodiments of a rocking mass in a rocking assembly
  • Figure 6 shows the divider of the swing assembly
  • FIG. 7 shows an enlarged view of a portion of a swing-type vibration damping device according to another embodiment of the present disclosure
  • Fig. 8 shows a swing block in the swing assembly of Fig. 7;
  • FIG. 9 shows a divider in the swing assembly of FIG. 7 .
  • the swing-type vibration damping device includes a support plate 1 rotatable about a rotation axis RO, a swing assembly 2 , a rolling member 3 and a stopper 4 .
  • the oscillating vibration damping device includes three oscillating assemblies 2 evenly distributed along the circumferential direction on the support plate 1 . It can be understood that the number of swing assemblies 2 can be varied.
  • the swing assembly 2 includes a first swing block 2a and a second swing block 2b arranged on axially opposite sides of the support plate 1, respectively, and a partition 5 arranged between the two swing blocks.
  • the configurations of the first swing block 2a and the second swing block 2b may be completely the same. Therefore, hereinafter, the configuration of the wobble block will be described in detail with respect to the first wobble block 2a. It can be understood that the description of the first swinging block 2a below is also applicable to the second swinging block 2b.
  • the first swing block 2a and the second swing block 2b are connected together, and both are connected to the partition 5 .
  • the support plate 1 is provided with an inner recess 11 which is recessed radially outward on its inner circumference.
  • the separator 5 is arranged in the recess 11 so as to be embedded.
  • the rolling elements 3 are likewise arranged in said inner recess 11 .
  • the rolling members 3 are formed of cylindrical rollers having a circular cross-section.
  • the bottom surface of the inner recess 11 defines the first rolling track 12
  • the partition 5 defines the second rolling track 51 .
  • the rolling member 3 is sandwiched between the first rolling track 12 and the second rolling track 51 .
  • each swing assembly 2 of the swing type vibration damping device corresponds to two rolling members 3 .
  • the bottom surface of the inner recess 11 defines two first rolling tracks 12
  • the spacer 5 defines two second rolling tracks 51 .
  • the two first rolling tracks 12 are symmetrical with respect to the axial center plane of the inner recess
  • the two second rolling tracks 51 are symmetrical about the axial center plane of the spacer 5 . It should be understood that the number of the rolling members 3 corresponding to each swing assembly 2 can also be varied.
  • the first rocking block 2a is provided with a first connecting protrusion 21 and a first connecting groove 22 on its outer circumference.
  • the second rocking block 2b is also provided with a first connecting protrusion 21 and a first connecting groove 22 on its outer circumference.
  • the positions of the first connecting protrusion 21 and the first connecting groove 22 are symmetrical with respect to the axial center plane of the rocking block.
  • the width of the main body portion of the first connecting protrusion 21 is slightly larger than the width of the first connecting groove 22, and the two form an interference fit, thereby firmly connecting the first swing block 2a and the second swing block 2b together.
  • the first connecting protrusion 21 has a chamfer 23 on the end so that the width of the tip portion of the first connecting protrusion 21 is smaller than that of the first connecting groove 22 Therefore, the interference fit between the first connecting protrusion 21 and the first connecting groove 22 can be guided.
  • the support disc 1 is provided on its outer circumference with an outer recess 13 which is recessed radially inward, and the first connecting protrusion 21 spans the support disc 1 in the outer recess 13 .
  • the support plate 1 is provided with two outer recesses 13 to correspond to the first connection protrusions 21 of the first swing block 2a and the second swing block 2b, respectively.
  • the bottom surface of the outer recess 13 of the support plate 1 forms the anti-fall surface 14 of the swing assembly 2 .
  • the first connecting protrusions 21 may be radially supported on the anti-drop surface 14 , thereby preventing the swing assembly 2 from falling radially inward toward the center of the support plate 2 . This reduces the noise generated by the oscillating damper when the engine is started and stopped. After the engine is started, the pendulum assembly 2 is biased radially outward under the action of centrifugal force. When the rotation speed of the support disc 1 about the axis RO exceeds a predetermined threshold, the first connecting protrusions 21 come out of contact with the anti-fall surface 14 , which allows the swing assembly 2 to swing freely relative to the support disc 1 .
  • the anti-drop surface 14 has a dynamic shape.
  • the contour of the anti-fall surface 14 is designed in relation to the first rolling track 12, the second rolling track 51, so that when the rolling member 3 moves along the first rolling track 12, the first connecting protrusion 21 follows the The contour of the anti-drop surface 14 . That is, when the swing type vibration damping device operates, there is a gap between the first connecting protrusion 21 and the anti-falling surface 14, and the minimum gap range is constant. For example, the minimum gap range is 0.2-0.8 mm.
  • both the first swing block 2a and the second swing block 2b are provided with two retaining holes 24 .
  • the two stop holes 24 are symmetrical with respect to the axial center plane of the oscillating block.
  • the stopper holes 24 of the first swing block 2a and the second swing block 2b are aligned with each other, and the stopper 4 is inserted into the stopper holes 24.
  • the divider 5 comprises, on its opposite sides, two narrowings 52 symmetrical with respect to its axial central plane, which are supported on said stops 4 so as to be able to restrain the divider 5 in the swing assembly 2 s position. It can be understood that, the side surface of the partition member 5 may not include the narrowed portion, but is directly supported on the stopper member 4 .
  • the first and second rocking blocks 2 a and 2 b of the rocking assembly 2 are also connected to the partition 5 radially inside.
  • the first rocking block 2 a is further provided with two punching bosses 25 at its radially inner center portion, and the punching bosses 25 are formed by punching, for example.
  • the two punching bosses 25 are respectively provided with punching rivets 26 and punching grooves 27 .
  • FIG. 5B shows another embodiment of the stamping boss 25 .
  • the first swinging block 2a includes only one punching boss 25 on which punching rivets 26 and punching grooves 27 are formed.
  • the second swinging block 2b may also have similar punching bosses 25 , punching rivets 26 and punching grooves 27 . It can be understood that, only one of the punched rivets 26 and punched grooves 27 may be provided on the first swing block 2a, and the other of the punched rivets 26 and the punched grooves 27 may be provided at complementary positions on the second swing block 2b. .
  • the punching boss 25 By forming the punching boss 25 first, the axial side surface of the first rocking block 2a is flattened, thereby facilitating the punching operation for forming the punched rivet 26 and the punched groove 27 . It can be understood that, instead of forming a punching boss, punching rivets 26 and punching grooves 27 can be punched directly on the swing block.
  • the spacer 5 is provided with countersunk recesses 53 on two axially opposite sides thereof. Although only a countersunk recess 53 is shown in FIG. 6 that is recessed on one side of the divider 5, it will be understood that the divider 5 also includes another countersunk recess that is recessed in the opposite direction on the opposite side 53.
  • the bottom surface of the countersunk recess 53 includes, for example, a rivet hole 54 formed by punching.
  • the rivet head of the punched rivet 26 passing through the rivet hole 54 is accommodated in the countersunk recess 53 without protruding from the axial side of the rocker. Furthermore, when the swing assembly 2 is assembled, the punched rivets 26 of the first swing block 2a, the rivet holes 54 of the spacer 5 and the punched grooves 27 of the second swing block 2b are aligned with each other. vice versa.
  • the punched groove 27 allows the riveting tool to directly contact the rivet head of the punched rivet 26 , facilitating the riveting of the punched rivet 26 to the rivet hole 54 .
  • the first rocking block 2 a further has, on its axial side surface facing the support plate 1 , a separation boss 28 protruding from the side surface.
  • the separation boss 28 can reduce the contact area between the first swing block 2a and the support plate 1 on the axial side surface, and reduce friction between the two.
  • the inner concave portion 11 and the outer concave portion 13 of the support plate 1 can also be used to limit the movement range of the swing assembly 2 of the swing type vibration damping device.
  • the side surface of the inner recess 11 contacts the side surface of the partition 5 to prevent the swing assembly 2 from further swinging.
  • the outer recess 13 is provided with stop surfaces 15 at both ends of the anti-fall surface 14 .
  • the stop surface 15 contacts with the first connecting protrusion 21 to prevent the swing assembly 2 from further swinging.
  • the two first connecting protrusions 21 and the two stop surfaces 15 of the first swing block 2 a and the second swing block 2 b , as well as the side surface of the inner recess 11 and the side surface of the partition 5 form 3 mechanical stop mechanisms.
  • These three mechanical stop mechanisms work simultaneously to limit the relative movement range between the swing assembly 2 and the support plate 1 . This can also avoid excessive compression of the stopper 4 by the spacer 5 and protect the stopper 4 .
  • the mechanical force can also be dispersed on the three mechanical stop mechanisms to avoid mechanical damage.
  • connection between the first swing block 2a and the second swing block 2b of the swing assembly 2 and the spacer 5 is also realized by the interference fit between the connection protrusion and the connection groove.
  • the first rocking block 2a is provided with two second connecting grooves 29 at its radially inner circumference
  • the spacer 5 is provided with two second connecting grooves 29 protruding in opposite directions at its radially inner circumference.
  • the second connecting protrusion 55 When assembling the swing assembly 2, the two second connection protrusions 55 of the spacer 5 are respectively inserted into the second connection grooves 29 of the first swing block 2a and the second swing block 2b in the manner of interference fit described in detail above, Thereby, the partition 5 is connected with the first swing block 2a and the second swing block 2b.
  • first swing block 2a and the second swing block 2b may be provided with only one second connection groove 29 at a position corresponding to the second connection protrusion 55 .
  • Providing two second connecting grooves 29 symmetrical with respect to their axial center planes on the first rocking block 2a and the second rocking block 2b can improve the versatility of components.
  • the riveting step for connecting the swing block and the spacer can be further omitted during the assembly process of the swing type vibration damping device shown in FIG. 7 to FIG.
  • the second connecting groove can also be provided at the radially inner circumference of the partition 5, and the first rocking block 2a and the second rocking block A second connecting protrusion is respectively provided at the complementary position of 2b.

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  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
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  • Vibration Prevention Devices (AREA)

Abstract

一种摆动式减振装置，其包括：支撑盘（1）、至少一个摆动组件（2）和滚动构件（3）。摆动组件（2）包括第一摆动块（2a）和第二摆动块（2b），以及分隔件（5）。滚动构件（3）被夹持在由支撑盘（1）限定的第一滚动轨道（12）和由分隔件（5）限定的第二滚动轨道（51）之间。第一摆动块（2a）和第二摆动块（2b）由过盈配合的连接槽（22，29）和连接突起（21，55）连接在一起。还提供包括摆动式减振装置的液力变矩器、离合器盘、双质量飞轮和机动车辆。

Description

摆动式减振装置和包括其的机动车辆 技术领域
本公开涉及一种摆动式减振装置。本公开还涉及包括所述摆动式减振装置的液力变矩器、离合器盘、双质量飞轮或机动车辆。
背景技术
机动车辆发动机产生的扭矩通常是不恒定的。这种不恒定的扭矩可被传递到变速器齿轮箱中，造成变速器齿轮箱的振动，并且因而产生特别不期望的噪音或撞击等。为了减少振动的不利影响并且提高机动车辆的驾驶舒适性，在汽车传动系的扭矩传递装置中配备扭转减振装置是已知的。扭转减振装置可以允许吸收并减轻汽车发动机产生的振动。
一种已知的扭转减振装置是摆动式减振装置，其具有能够围绕旋转轴线枢转的支承件，以及安装在支承件上布置的摆动块。在发动机产生的转速发生变化时，摆动块可在一定范围内围绕旋转轴线相对支承件摆动，从而通过摆动块的惯性作用吸收并减轻汽车发动机产生的振动。
通常地，为了使得摆动块能够相对支承件摆动，支承件与摆动块之间布置有与二者同时滚动接触的滚动元件。在摆动式减振装置的运行过程中，摆动块径向地支承在滚动元件上，而滚动元件本身径向地支承在支承件上。同时，摆动块通常成对设置，成对的摆动块通常通过铆钉连接在一起，并将支承件夹持在其间，从而能够在轴向方向上约束摆动块，同时不阻碍摆动块相对支撑件绕旋转轴线的摆动。但是，摆动式减振装置通常包括沿周向方向布置的多对摆动块，因而需要提供多个铆钉以连接摆动块。特别地，摆动式减振装置通常需要采用较为昂贵的专用铆钉，这显著增加了摆动式减振装置的成本。同时，连接摆动块的额外铆接操作也增加了组装摆动式减振装置的步骤，提高了生产成本。
发明内容
因此，本公开旨在解决常规的摆动式减振装置中存在的上述问题，其目的在于提供一种摆动式减振装置，其中摆动式减振装置的摆动块无需通过铆钉进行连接。这种摆动式减振装置能够降低部件的复杂度，减少部件数量， 便于制造并降低了成本。
所述目的是通过根据本公开的一个实施例的摆动式减振装置实现的。所述摆动式减振装置包括：能够围绕轴线旋转的支撑盘；相对于所述支撑盘可移动的至少一个摆动组件，所述摆动组件包括分别布置在所述支撑盘的轴向相对侧上的第一摆动块和第二摆动块，以及布置在第一摆动块和第二摆动块之间并连接第一摆动块和第二摆动块的分隔件；至少一个滚动构件，所述滚动构件被夹持在由支撑盘限定的第一滚动轨道和由所述分隔件限定的第二滚动轨道之间。第一摆动块和第二摆动块的一个上设置有第一连接槽，所述第一摆动块和第二摆动块的另一个上设置有第一连接突起，所述第一连接突起以过盈配合的方式插入所述第一连接槽，以将第一摆动块和第二摆动块连接在一起。
由此，根据本公开的摆动式减振装置的摆动组件的两个摆动块通过过盈配合的连接突起和连接槽连接，从而无需用于铆接的铆钉。因此，根据本公开的摆动式减振装置能够降低部件的复杂度，减少部件数量，降低零部件成本。同时，通过省去铆接步骤，根据本公开的摆动式减振装置的组装也得以简化，降低了生产成本。
根据本公开的摆动式减振装置还可以单独或组合地具有以下特征中的一个或多个。
根据本公开的一个可选实施例，所述支撑盘在其外周上设置有与所述第一连接突起配合的抗跌落表面。据此，在机动车辆的发动机启动和停机时，所述第一连接突起可以支撑在所述抗跌落表面上，从而防止摆动组件跌落，进而减少分隔件和滚动元件之间的噪音，以及分隔件和支撑件之间的噪音。
根据本公开的一个可选实施例，在所述支撑盘围绕轴线旋转的转速超过预定阈值时，所述抗跌落表面与所述第一连接突起之间存在间隙。优选地，所述预定阈值小于发动机启动后的最低转速。也就是说，当机动车辆的发动机启动后，摆动组件在离心力的作用下沿径向向外移动，使得抗跌落表面与第一连接突起脱离接触，从而消除二者之间的摩擦产生的噪音，并避免摩擦对支撑盘和摆动组件导致的损坏。
根据本公开的一个可选实施例，当所述滚动构件沿第一滚动轨道运动时，所述第一连接突起遵循所述抗跌落表面的轮廓。优选地，当所述滚动构件沿第一滚动轨道运动时，所述第一连接突起与所述抗跌落表面之间的最小 间隙范围是恒定的。也就是说，当摆动组件相对于支撑盘摆动时，第一连接突起所遵循的运动轨迹与抗跌落表面的轮廓相互匹配，使得第一连接突起与抗跌落表面之间的距离位于恒定的最小间隙范围内。
根据本公开的一个可选实施例，所述支撑盘在所述抗跌落表面的两端设置有止挡面。据此，当摆动式减振装置的摆动组件达到其最大位移时，所述第一连接突起与所述止挡面接触，限制所述摆动组件与支撑盘之间相对运动的范围。
根据本公开的一个可选实施例，所述支撑盘在其内周上设置有径向向外凹入的内凹部，所述分隔件位于所述内凹部内，并且所述第一滚动轨道由所述内凹部的底面限定。所述内凹部与所述分隔件合作，限制所述摆动组件与支撑盘之间相对运动的范围。也就是说，当摆动式减振装置的摆动组件达到其最大位移时，所述内凹部的侧面与分隔件接触，从而限制所述摆动组件与支撑盘之间相对运动的范围。
根据本公开的一个可选实施例，所述第一摆动块和第二摆动块上都设置有两个止动孔，并且所述第一摆动块和第二摆动块上的止动孔彼此对准，用于插入两个止动件，所述止动件约束分隔件在摆动组件中的位置。
根据本公开的一个可选实施例，所述第一摆动块和第二摆动块中的至少一个摆动块还设置有冲压铆钉，并且所述分隔件设置有与所述冲压铆钉对齐的铆钉孔。优选地，所述第一摆动块和第二摆动块都设置有冲压铆钉，并且所述分隔件设置有两个铆钉孔，分别与所述第一摆动块和第二摆动块的冲压铆钉对齐。据此，所述第一摆动块和/或第二摆动块分隔件能够与分隔件连接在一起。
根据本公开的一个可选实施例，所述至少一个摆动块还设置有冲压凸台，所述冲压铆钉位于所述冲压凸台上。可选地，所述冲压凸台和冲压铆钉在不同的冲压步骤中形成。优选地，所述至少一个摆动块先通过冲压形成冲压凸台，然后再对所述冲压凸台进行冲压，以形成冲压铆钉。先形成冲压凸台可以得到平整的表面，有利于控制所述冲压铆钉的朝向。
根据本公开的一个可选实施例，所述分隔件设置有沉头凹部，所述铆钉孔布置在所述沉头凹部中。据此，在完成冲压铆钉到铆钉孔的铆接之后，铆钉头不会突出超过所述沉头凹部，从而不会影响两个摆动块之间的连接。
根据本公开的一个可选实施例，所述第一摆动块和第二摆动块中的至少 另一个摆动块上还设置有冲压槽，所述冲压槽、所述铆钉孔和所述冲压铆钉彼此对齐。
根据本公开的一个可选实施例，所述第一摆动块和第二摆动块中的至少一个摆动块还设置有第二连接槽，并且所述分隔件设置有以过盈配合的方式插入所述第二连接槽的第二连接突起。可选地，所述第一摆动块和第二摆动块中的至少一个摆动块还设置有第二连接突起，所述第二连接突起以过盈配合的方式插入设置在所述分隔件上的第二连接槽。根据上述技术方案，摆动块与分隔件之间的连接也通过连接突起和连接槽的方式实现，而不是通过冲压铆钉和铆钉孔。
根据本公开的一个可选实施例，所述第一摆动块和第二摆动块中的至少一个摆动块在其轴向面对支撑盘的侧面上具有从该侧面凸起的分隔凸台。据此，摆动块与支撑盘的侧面仅在所述分隔凸台处发生接触，从而避免了摆动块与支撑盘之间的大面积接触。
根据本公开的一个可选实施例，所述第一连接突起在端部上具有倒角。优选地，所述第二连接突起在端部上也具有倒角。所述倒角可以引导连接突起与连接槽之间的过盈配合，并且也可以容纳连接突起和连接槽上的毛刺。
根据本公开的一个可选实施例，所述支撑盘、所述第一摆动块、所述第二摆动块和所述分隔件中的至少一个通过冲压的方式制造。优选地，所述支撑盘、所述第一摆动块、所述第二摆动块和所述分隔件全部通过冲压的方式制造。
根据本公开的一个可选实施例，所述支撑盘、所述第一摆动块、所述第二摆动块和所述分隔件中的至少一个通过冲压的方式制造。
本公开还提供一种液力变矩器，其包括如上所述的摆动式减振装置。
本公开还提供一种双质量飞轮，其包括如上所述的摆动式减振装置。
本公开还提供一种离合器盘，其包括如上所述的摆动式减振装置。
本公开还提供一种机动车辆，其包括如上所述的摆动式减振装置、液力变矩器、双质量飞轮和离合器盘中的至少一个。
附图说明
本公开的上述和其他特征以及优点将通过下面的结合附图的示例性实施例的详细描述变得更加明显，并且该描述和附图仅用于示例性目的而不是 以任何方式来限制本公开的范围，图中：
图1是根据本公开的一个实施例的摆动式减振装置的透视图；
图2是图1所示的摆动式减振装置的分解视图；
图3A和图3B是图1所示的摆动式减振装置的一部分的放大视图；
图4示出了摆动式减振装置的支撑盘；
图5A和图5B示出了摆动组件中的一个摆动块的两个实施例；
图6示出了摆动组件的分隔件；
图7示出了根据本公开另一实施例的摆动式减振装置的一部分的放大视图；
图8示出了图7的摆动组件中的一个摆动块；
图9示出了图7的摆动组件中的分隔件。
在所有附图中，相同或相似的部件用相同的编号指示。
具体实施方式
为了使本公开的实施例的目的、技术方案和优点更加清楚，下面将结合本公开实施例的附图对本公开的实施例的技术方案进行清楚、完整的描述。
除非另作定义，本文使用的技术术语或者科学术语应当为本公开所属领域内普通技术人员所理解的通常意义。本公开专利申请说明书以及权利要求书中使用的“一个”、“一”或者“该”等类似词语也不表示数量限制，而是表示存在至少一个。“包括”或者“包含”等类似的词语意指出现该词前面的元件或者物件涵盖出现在该词后面列举的元件或者物件及其等同物，而不排除其他元件或者物件。“轴向”、“径向”和“周向”等方向相对于摆动式减振装置的旋转轴线RO定义，轴向即旋转轴线RO延伸的方向，径向是与旋转轴线RO垂直的方向，而周向是围绕旋转轴线RO的圆周方向。
图1至图6示出了根据本公开一个实施例的摆动式减振装置。如图1和2所示，摆动式减振装置包括可围绕旋转轴线RO转动的支撑盘1、摆动组件2、滚动构件3和止动件4。在该实施例中，摆动式减振装置包括在支撑盘1上沿周向均匀分布的3个摆动组件2。可以理解的是，摆动组件2的数量是可以变化的。
摆动组件2包括分别布置在所述支撑盘1的轴向相对侧上的第一摆动块2a和第二摆动块2b、以及布置两个摆动块之间的分隔件5。第一摆动块2a 和第二摆动块2b的构造可以是完全相同的。因此，在下文中，将针对第一摆动块2a详细地描述摆动块的构造。可以理解的是，下文中对第一摆动块2a的描述同样适用于第二摆动块2b。
第一摆动块2a和第二摆动块2b连接在一起，并都连接至所述分隔件5。支撑盘1上设置有在其内周上径向向外凹入的内凹部11。所述分隔件5嵌入地布置在所述内凹部11内。滚动构件3同样布置在在所述内凹部11内。滚动构件3由具有圆形截面的圆柱形滚子形成。内凹部11的底面限定第一滚动轨道12，分隔件5限定第二滚动轨道51。滚动构件3被夹持在所述第一滚动轨道12和第二滚动轨道51之间。当摆动组件2在支承件1上摆动时，所述滚动构件3在所述第一滚动轨道12和第二滚动轨道51上滚动。
如图1和图2所示，摆动式减振装置的每个摆动组件2对应于两个滚动构件3。相应地，内凹部11的底面限定两个第一滚动轨道12，分隔件5限定两个第二滚动轨道51。所述两个第一滚动轨道12关于内凹部的轴向中心平面是对称的，并且两个第二滚动轨道51关于分隔件5的轴向中心平面是对称的。应当理解的是，每个摆动组件2所对应的滚动构件3的数量也是可以变化的。
参照图5A和图5B，第一摆动块2a在其外周上设置有第一连接突起21和第一连接槽22。类似地，第二摆动块2b在其外周上也设置有第一连接突起21和第一连接槽22。所述第一连接突起21和第一连接槽22的位置关于摆动块的轴向中心平面是对称的。在组装摆动组件2时，第一摆动块2a的第一连接突起21插入第二摆动块2b的第一连接槽22，并且第二摆动块2b的第一连接突起21插入第一摆动块2a的第一连接槽22。第一连接突起21的主体部分的宽度略大于第一连接槽22的宽度，二者形成过盈配合，从而将第一摆动块2a和第二摆动块2b牢固地连接在一起。为了便利于第一连接突起21到第一连接槽22之内的插入，第一连接突起21在端部上具有倒角23，使得第一连接突起21的尖端部分的宽度小于第一连接槽22的宽度，从而可以引导第一连接突起21与第一连接槽22之间的过盈配合。
参照图3A和3B，在连接形成摆动组件2之后，第一连接突起21的主体部分将在轴向方向上跨过支撑盘1。为此，支撑盘1在其外周上设置有径向向内凹入的外凹部13，所述第一连接突起21在外凹部13内跨过支撑盘1。对于每个摆动组件2，支撑盘1设置有两个外凹部13，以分别对应第一摆动 块2a和第二摆动块2b的第一连接突起21。
支撑盘1的外凹部13的底面形成摆动组件2的抗跌落表面14。第一连接突起21可以径向支撑在所述抗跌落表面14上，从而防止摆动组件2朝向支撑盘2的中心径向向内跌落。这可以减少摆动式减振装置在发动机启动和停机时产生的噪音。在发动机启动后，摆动组件2在离心力的作用下沿径向向外偏压。当支撑盘1围绕轴线RO旋转的转速超过预定阈值时，第一连接突起21与抗跌落表面14脱离接触，这使得摆动组件2可以相对于支撑盘1自由地摆动。抗跌落表面14具有动态的形状。特别地，所述抗跌落表面14的轮廓与第一滚动轨道12、第二滚动轨道51相关联地设计，使得在滚动构件3沿第一滚动轨道12运动时，所述第一连接突起21遵循抗跌落表面14的轮廓。也就是说，在摆动式减振装置运行时，第一连接突起21与抗跌落表面14之间具有间隙，且最小间隙范围是恒定。例如，所述最小间隙范围是0.2-0.8mm。
参照图2和图5A-图6，第一摆动块2a和第二摆动块2b都设置有两个止动孔24。所述两个止动孔24关于摆动块的轴向中心平面是对称的。在摆动组件2的组装构造中，第一摆动块2a和第二摆动块2b的止动孔24彼此对准，止动件4插入所述止动孔24中。分隔件5在其相对的侧面上包括关于其轴向中心平面对称的两个收窄部52，收窄部52支撑在所述止动件4上，从而能够约束分隔件5在摆动组件2中的位置。可以理解的是，分隔件5的侧面也可以不包括收窄部，而直接支撑在止动件4上。
除了通过止动件4约束分隔件5的位置，摆动组件2的第一摆动块2a和第二摆动块2b还在径向内部连接到分隔件5。参照图5A，第一摆动块2a还在其径向内中心部设置有两个冲压凸台25，所述冲压凸台25例如通过冲压形成。两个冲压凸台25上分别设置有冲压铆钉26和冲压槽27。图5B示出了冲压凸台25的另一实施例。在该实施例中，第一摆动块2a仅包括一个冲压凸台25，冲压铆钉26和冲压槽27都形成在所述冲压凸台25上。第二摆动块2b也可以具有类似的冲压凸台25、冲压铆钉26和冲压槽27。可以理解的是，也可以仅在第一摆动块2a上设置冲压铆钉26和冲压槽27中的一个，而在第二摆动块2b上的互补位置设置冲压铆钉26和冲压槽27中的另一个。
通过先形成冲压凸台25，第一摆动块2a的轴向侧面得以平整化，从而 有利于形成冲压铆钉26和冲压槽27的冲压操作。可以理解的是，也可以不形成冲压凸台，而直接在摆动块上冲压出冲压铆钉26和冲压槽27。
分隔件5则在其轴向相对的两个侧面上设置了沉头凹部53。虽然图6中仅示出了在分隔件5的一个侧面上凹入的沉头凹部53，但可以理解的是分隔件5还包括在在相对侧面上沿相反方向凹入的另一沉头凹部53。沉头凹部53的底面上包括例如通过冲压形成的铆钉孔54。在组装摆动组件2时，冲压铆钉26铆接到铆钉孔54内，从而将第一摆动块2a和第二摆动块2b与分隔件5连接在一起。冲压铆钉26的从铆钉孔54内穿过的铆钉头则容纳在沉头凹部53内，而不会从摆动块的轴向侧面突出。此外，在组装摆动组件2时，第一摆动块2a的冲压铆钉26、分隔件5的铆钉孔54和第二摆动块2b的冲压槽27彼此对齐。反之亦然。冲压槽27使得铆接工具可以直接接触冲压铆钉26的铆钉头，便利于冲压铆钉26到铆钉孔54的铆接。通过在摆动块上通过冲压形成冲压铆钉，可以节省使用常规铆钉的额外开支。
参见图5A和图5B，第一摆动块2a在其面对支撑盘1的轴向侧面上还具有从该侧面凸起的分隔凸台28。所述分隔凸台28可以减少，第一摆动块2a与支撑盘1在轴向侧面上的接触面积，减少二者之间的摩擦。
支撑盘1的所述内凹部11和外凹部13还可以用来限定摆动式减振装置的摆动组件2的运动范围。当摆动式减振装置的摆动组件2沿圆周方向摆动到其最大位移时，所述内凹部11的侧面与分隔件5的侧面接触，阻止摆动组件2的进一步摆动。类似地，外凹部13在抗跌落表面14的两端设置有止挡面15。当摆动式减振装置的摆动组件2沿圆周方向摆动到其最大位移时，所述止挡面15与第一连接突起21接触，阻止摆动组件2的进一步摆动。在图3A所示实施例中，第一摆动块2a和第二摆动块2b的两个第一连接突起21与两个止挡面15，以及内凹部11的侧面与分隔件5的侧面形成了3个机械止挡机构。这3个机械止挡机构同时起作用，以限制摆动组件2与支撑盘1之间相对运动的范围。这也可以避免分隔件5对止动件4的过度压缩，保护止动件4。此外，通过形成同时起作用的3个机械止挡机构，也可以将机械力在这3个机械止挡机构上进行分散，避免产生机械损伤。
图7至图9示出了根据本公开另一实施例的摆动式减振装置。与上文所述实施例的主要区别在于，摆动组件2的第一摆动块2a和第二摆动块2b与分隔件5之间的连接也通过连接突起和连接槽之间的过盈配合实现。
参考图8和图9，第一摆动块2a在其径向内周处设置有两个第二连接槽29，分隔件5则在其径向内周处设置有沿相反方向凸出的两个第二连接突起55。在组装摆动组件2时，分隔件5的两个第二连接突起55分别以上文所详述的过盈配合的方式插入到第一摆动块2a和第二摆动块2b的第二连接槽29，从而将分隔件5与第一摆动块2a和第二摆动块2b连接在一起。可以理解的是，第一摆动块2a和第二摆动块2b可以仅在与第二连接突起55对应的位置处设置一个第二连接槽29。在第一摆动块2a和第二摆动块2b上设置关于其轴向中心平面对称的两个第二连接槽29可以提高部件的通用性。通过过盈配合的连接突起和连接槽，图7至图9所示的摆动式减振装置的组装过程中可以进一步省去连接摆动块和分隔件的铆接步骤。
虽然未在附图中示出，但本领域技术人员可以设想的是，也可以将第二连接槽设置在分隔件5的径向内周处，并且在第一摆动块2a和第二摆动块2b的互补位置处分别设置一个第二连接突起。
应当理解的是，上面描述的和在附图中示出的结构仅是本公开的示例，其可通过表现出用于获得所需最终结果的相同或相似功能的其他结构代替。另外，应当理解的是，上面描述的和附图所示的实施例应被视为仅组成本公开的非限制性示例，并且它可在专利权利要求的范围内以多种方式进行修改。

Claims (22)

  1. 一种摆动式减振装置，其特征在于，所述摆动式减振装置包括：
    能够围绕轴线(RO)旋转的支撑盘(1)；
    相对于所述支撑盘(1)可移动的至少一个摆动组件(2)，所述摆动组件(2)包括分别布置在所述支撑盘(1)的轴向相对侧上的第一摆动块(2a)和第二摆动块(2b)，以及布置在所述第一摆动块(2a)和第二摆动块(2b)之间并连接第一摆动块(2a)和第二摆动块(2b)的分隔件(5)；
    至少一个滚动构件(3)，所述滚动构件(3)被夹持在由支撑盘(1)限定的第一滚动轨道(12)和由所述分隔件(5)限定的第二滚动轨道(51)之间，
    其中，所述第一摆动块(2a)和第二摆动块(2b)的一个上设置有第一连接槽(22)，所述第一摆动块(2a)和第二摆动块(2b)的另一个上设置有第一连接突起(21)，所述第一连接突起(21)以过盈配合的方式插入所述第一连接槽(22)，以将第一摆动块(2a)和第二摆动块(2b)连接在一起。
  2. 根据权利要求1所述的摆动式减振装置，其特征在于，
    所述支撑盘(1)在其外周上设置有与所述第一连接突起(21)配合的抗跌落表面(14)。
  3. 根据权利要求2所述的摆动式减振装置，其特征在于，
    在所述支撑盘(1)围绕轴线(RO)旋转的转速超过预定阈值时，所述抗跌落表面(14)与所述第一连接突起(21)之间存在间隙。
  4. 根据权利要求3所述的摆动式减振装置，其特征在于，
    当所述滚动构件(3)沿第一滚动轨道(12)运动时，所述第一连接突起(21)遵循所述抗跌落表面(14)的轮廓。
  5. 根据权利要求4所述的摆动式减振装置，其特征在于，
    当所述滚动构件(3)沿第一滚动轨道(12)运动时，所述第一连接突起(21)与所述抗跌落表面(14)之间的最小间隙范围是恒定的。
  6. 根据权利要求2所述的摆动式减振装置，其特征在于，
    所述支撑盘(1)在所述抗跌落表面(14)的两端设置有止挡面(15)。
  7. 根据权利要求1至6中的任一项所述的摆动式减振装置，其特征在于，
    所述支撑盘(1)在其内周上设置有径向向外凹入的内凹部(11)，所述分隔件(5)位于所述内凹部(11)内，并且所述第一滚动轨道(12)由所述内凹部(11)的底面限定。
  8. 根据权利要求7所述的摆动式减振装置，其特征在于，
    所述内凹部(11)与所述分隔件(5)合作，限制所述摆动组件(2)与支撑盘(1)之间相对运动的范围。
  9. 根据权利要求1至6中的任一项所述的摆动式减振装置，其特征在于，
    所述第一摆动块(2a)和第二摆动块(2b)上都设置有两个止动孔(24)，并且所述第一摆动块(2a)和第二摆动块(2b)上的止动孔(24)彼此对准，用于插入两个止动件(4)，所述止动件(4)约束分隔件(5)在摆动组件(2)中的位置。
  10. 根据权利要求1至6中的任一项所述的摆动式减振装置，其特征在于，
    所述第一摆动块(2a)和第二摆动块(2b)中的至少一个摆动块还设置有冲压铆钉(26)，并且所述分隔件(5)设置有与所述冲压铆钉(26)对齐的铆钉孔(54)。
  11. 根据权利要求10所述的摆动式减振装置，其特征在于，
    所述至少一个摆动块还设置有冲压凸台(25)，所述冲压铆钉(26)位于所述冲压凸台(25)上。
  12. 根据权利要求10所述的摆动式减振装置，其特征在于，
    所述分隔件(5)设置有沉头凹部(53)，所述铆钉孔(54)布置在所述沉头凹部(53)中。
  13. 根据权利要求10所述的摆动式减振装置，其特征在于，
    所述第一摆动块(2a)和第二摆动块(2b)中的至少另一个摆动块上还设置有冲压槽(27)，所述冲压槽(27)、所述铆钉孔(54)和所述冲压铆钉(26)彼此对齐。
  14. 根据权利要求1至6中的任一项所述的摆动式减振装置，其特征在于，
    所述第一摆动块(2a)和第二摆动块(2b)中的至少一个摆动块还设置有第二连接槽(29)，并且所述分隔件(5)设置有以过盈配合的方式插入所 述第二连接槽(29)的第二连接突起(55)。
  15. 根据权利要求1至6中的任一项所述的摆动式减振装置，其特征在于，
    所述第一摆动块(2a)和第二摆动块(2b)中的至少一个摆动块还设置有第二连接突起(55)，所述第二连接突起(55)以过盈配合的方式插入设置在所述分隔件(5)上的第二连接槽(29)。
  16. 根据权利要求1至6中的任一项所述的摆动式减振装置，其特征在于，
    所述第一摆动块(2a)和第二摆动块(2b)中的至少一个摆动块在其轴向面对支撑盘(1)的侧面上具有从该侧面凸起的分隔凸台(28)。
  17. 根据权利要求1至6中的任一项所述的摆动式减振装置，其特征在于，
    所述第一连接突起(21)在端部上具有倒角(23)。
  18. 根据权利要求1至6中的任一项所述的摆动式减振装置，其特征在于，
    所述支撑盘(1)、所述第一摆动块(2a)、所述第二摆动块(2b)和所述分隔件(5)中的至少一个通过冲压的方式制造。
  19. 一种液力变矩器，其特征在于，所述液力变矩器包括根据权利要求1至18中任一项所述的摆动式减振装置。
  20. 一种双质量飞轮，其特征在于，所述双质量飞轮包括根据权利要求1至18中任一项所述的摆动式减振装置。
  21. 一种离合器盘，其特征在于，所述离合器盘包括根据权利要求1至18中任一项所述的摆动式减振装置。
  22. 一种机动车辆，其特征在于，所述机动车辆包括根据权利要求1至18中任一项所述的摆动式减振装置、根据权利要求19所述的液力变矩器、根据权利要求20所述的双质量飞轮和根据权利要求21所述的离合器盘中的至少一个。
PCT/CN2021/141989 2020-12-31 2021-12-28 摆动式减振装置和包括其的机动车辆 WO2022143636A1 (zh)

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