CN108730409B

CN108730409B - Automobile and dual mass flywheel

Info

Publication number: CN108730409B
Application number: CN201710262393.7A
Authority: CN
Inventors: 葛凤龙; 葛柱洪
Original assignee: SAIC Motor Corp Ltd
Current assignee: SAIC Motor Corp Ltd
Priority date: 2017-04-20
Filing date: 2017-04-20
Publication date: 2020-05-01
Anticipated expiration: 2037-04-20
Also published as: CN108730409A

Abstract

An automobile and a dual-mass flywheel, wherein the dual-mass flywheel comprises a main flywheel and an auxiliary flywheel which are sequentially arranged along the axial direction; an elastic damping mechanism and a clutch piece are arranged between the main flywheel and the auxiliary flywheel, and the elastic damping mechanism can generate elastic deformation when the main flywheel and the auxiliary flywheel rotate relatively; the clutch part comprises a fixed part and a movable part, one of the movable part and the fixed part is connected with the main flywheel, the other one of the movable part and the fixed part is connected with the auxiliary flywheel, and the movable part and the fixed part are arranged oppositely and can move relative to the fixed part along the radial direction of the dual-mass flywheel; the movable piece and the fixed piece can be combined to enable the main flywheel and the auxiliary flywheel to synchronously rotate; and the movable piece can be separated from the fixed piece under the action of gradually increasing centrifugal force along with the increase of the rotating speed of the dual-mass flywheel so as to separate the main flywheel and the auxiliary flywheel. The dual-mass flywheel of the technical scheme can reduce the resonance risk when the engine rotates at a low speed.

Description

Automobile and dual mass flywheel

Technical Field

The invention relates to the technical field of automobiles, in particular to an automobile and a dual-mass flywheel.

Background

The conventional automobile transmission system generally comprises a dual-mass flywheel, and the dual-mass flywheel is used for transmitting the output torque of an engine and can reduce the torsional vibration generated when the engine rotates. A conventional dual mass flywheel may include a primary flywheel, a secondary flywheel, and a resilient damping mechanism therebetween. The dual-mass flywheel is connected to the output end of the engine through the main flywheel and connected to the input end of the gearbox through the auxiliary flywheel, and the main flywheel and the auxiliary flywheel are connected through a bearing so that the main flywheel and the auxiliary flywheel can rotate relatively. The torque output by the engine is transmitted from the main flywheel to the elastic damping mechanism, and the elastic damping mechanism further transmits the torque to the auxiliary flywheel.

In the process, the elastic vibration damping mechanism can be elastically deformed to achieve the purpose of vibration damping. Therefore, the main flywheel and the auxiliary flywheel are elastically connected through the elastic damping mechanism, so that the resonance frequency of the dual-mass flywheel can be reduced, for example, the resonance frequency can be reduced to be lower than the resonance frequency of the engine during idle rotation. When the engine rotates at a high speed, such as above idle speed, the Vibration frequency of the engine is larger than the resonance frequency of the dual-mass flywheel, so that the transmission system of the dual-mass flywheel does not resonate, and the automobile has good NVH (noise Vibration harshness) performance.

However, under certain specific conditions of the engine, such as engine starting, idle rotation of the engine, and low engine speed, the vibration frequency generated by the rotation of the engine approaches or reaches the resonance frequency of the dual-mass flywheel to cause system resonance, and the resonance can generate large impact, so that the service life of the dual-mass flywheel and the surrounding parts is reduced and even damaged.

Therefore, how to reduce the risk of resonance of the dual mass flywheel at low engine speed is a great problem to be solved in the industry.

Disclosure of Invention

The invention solves the problem of how to reduce the resonance risk of the dual-mass flywheel at the low rotating speed of the engine.

To solve the above problems, the present invention provides a dual mass flywheel. The dual-mass flywheel comprises a main flywheel and an auxiliary flywheel which are sequentially arranged along the axial direction;

an elastic damping mechanism and a clutch piece are arranged between the main flywheel and the auxiliary flywheel, and the elastic damping mechanism can elastically deform when the main flywheel and the auxiliary flywheel rotate relatively;

the clutch piece comprises a fixed piece and a movable piece, one of the movable piece and the fixed piece is connected to the main flywheel, the other one of the movable piece and the fixed piece is connected to the auxiliary flywheel, and the movable piece and the fixed piece are arranged opposite to each other and can move relative to the fixed piece along the radial direction of the dual-mass flywheel;

the movable piece and the fixed piece can be combined to enable the main flywheel and the auxiliary flywheel to synchronously rotate; and the movable piece can be separated from the fixed piece under the action of gradually increasing centrifugal force along with the increase of the rotating speed of the dual-mass flywheel, so that the main flywheel and the auxiliary flywheel are separated.

Optionally, one of the movable member and the fixed member is provided with an insertion portion and the other is provided with a receiving portion;

when the inserting part is inserted into the accommodating part, the movable piece is combined with the fixed piece;

when the insertion part is not inserted into the containing part, the movable piece and the fixed piece are separated.

Alternatively, the movable member has an inner peripheral surface facing the fixed member, and the fixed member has an outer peripheral surface facing the movable member; one of the insertion portion and the housing portion is provided on the inner peripheral surface and the other is provided on the outer peripheral surface.

Optionally, the receiving portion is a slot or a jack.

Optionally, the accommodating portion extends in the circumferential direction of the dual mass flywheel to form an arc.

Optionally, the fixed member is provided with first engaging teeth facing the movable member, and all the first engaging teeth are arranged along the circumferential direction of the dual mass flywheel; the movable piece is provided with a plurality of second combination teeth facing the fixed piece, and all the second combination teeth are arranged along the circumferential direction; the first combining tooth and the second combining tooth can be meshed to combine the movable piece and the fixed piece; the first combination tooth and the second combination tooth can be separated, so that the movable piece and the fixed piece can be separated.

Optionally, the first coupling tooth and the second coupling tooth are both involute teeth.

Optionally, a base is arranged between the main flywheel and the auxiliary flywheel, the base is fixed to the auxiliary flywheel, and the fixing member is fixed to the main flywheel and penetrates through the base;

the movable piece is arranged on at least one side of the base body along the axial direction, and the movable piece is movably connected with the base body to realize the radial movement.

Optionally, the movable members are divided into at least one pair, each pair of movable members comprising: the movable pieces are positioned on two sides of the base body along the axial direction and connected together, and the movable pieces on at least one side along the axial direction can be separated from or combined with the fixed pieces.

Optionally, the active connection comprises:

one of the base body and the movable piece is provided with a track hole;

the other of the base body and the movable piece is provided with a through hole;

and a pin penetrates through the track hole and the through hole to connect the base body and the movable piece, and the pin can slide along the wall of the track hole in the radial direction to enable the movable piece to move in the radial direction.

Optionally, at least two of the track holes corresponding to at least one of the movable members are arranged along the circumferential direction.

Optionally, two track holes are arranged corresponding to each movable member and arranged along the circumferential direction;

from inside to outside along the radial direction, the distance between the two track holes corresponding to each movable piece is firstly reduced and then increased;

the through holes are linear holes, at least two through holes which are arranged in parallel along the radial direction are arranged corresponding to each movable piece, each through hole is always overlapped with at least two track holes to allow the pin to pass through, and when the pin can slide along the hole wall of the track hole along the radial direction, the pin can slide along the hole wall of the linear hole along the length direction of the through hole passing through.

Optionally, the track hole is in a variable-curvature arc shape, and the curvature increases and then decreases from inside to outside along the radial direction; in the circumferential direction, one of the two track holes corresponding to each movable member protrudes toward the other track hole, and the convex point has the largest curvature.

Optionally, the two track holes corresponding to each movable element are symmetrically arranged.

Optionally, the movable members are disposed on both sides of the base body in the axial direction, and each pin penetrates through the base body and the movable members on both sides of the base body in the axial direction.

Optionally, the movable member has at least two arranged around the fixed member along the circumferential direction.

The invention also provides an automobile. The vehicle comprising an engine, a gearbox and a dual mass flywheel as claimed in any one of claims 1 to 16, the dual mass flywheel being connected to the output of the engine via the primary flywheel and to the input of the gearbox via the secondary flywheel.

Compared with the prior art, the technical scheme of the invention has the following advantages:

one of the fixed piece and the movable piece is connected with the main flywheel, the other one of the fixed piece and the movable piece is connected with the auxiliary flywheel, and the movable piece is arranged opposite to the fixed piece and can move relative to the fixed piece along the radial direction of the dual-mass flywheel. The fixed member and the movable member are radially separable from and engageable with each other.

The dual mass flywheel receives the output torque of the engine through the main flywheel, and when the engine speed is low, such as idling speed or below, the rotating speed of the dual mass flywheel is low, and the generated centrifugal force is not enough to enable the movable piece to move outwards in the radial direction, so that the movable piece and the fixed piece are kept combined. In the process, the main flywheel and the auxiliary flywheel are in rigid connection, the elastic damping mechanism cannot generate elastic deformation, and the resonance frequency of the dual-mass flywheel system is higher. At this time, the vibration frequency generated by the low-speed rotation of the engine is lower than the resonance frequency, so that the resonance of a transmission system such as a dual mass flywheel is not caused. This can reduce or even avoid the generation of a large impact, and is advantageous in extending the life of the dual mass flywheel and its surrounding components.

When the engine rotates at a high speed, such as above idle speed, the movable part is subjected to a large centrifugal force and moves outwards in the radial direction to be separated from the fixed part, and the movable part and the fixed part are elastically connected through the elastic damping mechanism, and the elastic damping mechanism can be elastically deformed, so that the resonance frequency of the system is reduced. Therefore, the vibration frequency generated when the engine rotates at a high rotation speed can be higher than the resonance frequency, and thus the system does not resonate.

Further, when the engine is driven from a high speed to a low speed, the movable member can move inward in the radial direction due to the reduction of the centrifugal force applied to the movable member until the movable member and the stationary member are recombined. Therefore, the dual-mass flywheel of the technical scheme not only meets the anti-resonance requirement when the engine rotates at a high speed, but also can meet the anti-resonance requirement when the engine rotates at a low rotating speed.

Drawings

FIG. 1 is an exploded view of a dual mass flywheel according to a first embodiment of the present invention;

FIG. 2 is a perspective view of a stationary member of the dual mass flywheel of FIG. 1;

FIG. 3 is a perspective view of the dual mass flywheel of FIG. 1 with the movable member assembled with the base;

FIG. 4 is a perspective view of the base shown in FIG. 3;

FIG. 5 is an enlarged view of area A of FIG. 3;

fig. 6 is a schematic view showing the fitting relationship between the movable member and the stationary member in the dual mass flywheel of the second embodiment of the present invention.

Detailed Description

In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in detail below.

First embodiment

The automobile comprises an engine, a gearbox and a dual-mass flywheel connected between the engine and the gearbox, wherein the dual-mass flywheel can transfer the output torque of the engine to the gearbox. Referring to fig. 1, the dual mass flywheel may include a main flywheel 1 and an auxiliary flywheel 2 sequentially arranged along an axial direction, an elastic damping mechanism 3 and a clutch member may be disposed between the main flywheel 1 and the auxiliary flywheel 2, and the elastic damping mechanism 3 may elastically deform when the main flywheel 1 and the auxiliary flywheel 2 relatively rotate, so as to achieve the purpose of damping vibration.

The clutch member includes a fixed member 4 and a movable member 5, one of the movable member 5 and the fixed member 4 is connected to the main flywheel 1 and the other is connected to the sub flywheel 2, which may include: the stator 4 is provided on the sub flywheel 2 and the mover 5 is provided on the main flywheel 1. Along the radial direction of the dual-mass flywheel, the movable piece 5 is arranged opposite to the fixed piece 4, and the movable piece 5 can move relative to the fixed piece 4;

the fixed member 4 and the movable member 5 can be combined so that the main flywheel 1 and the sub flywheel 2 can rotate synchronously; and the movable member 5 can be separated from the fixed member 4 under the action of the centrifugal force which is gradually increased along with the increase of the rotating speed of the dual mass flywheel, so that the main flywheel 1 and the auxiliary flywheel 2 are separated.

The dual mass flywheel receives the output torque of the engine through the primary flywheel 1, and at low engine speeds, for example at or below idle speed, the rotational speed of the dual mass flywheel is low and the centrifugal force generated is not sufficient to move the movable member 5 radially outward, so that the movable member 5 and the stationary member 4 remain coupled. In the process, the main flywheel 1 and the auxiliary flywheel 2 are in rigid connection, the elastic damping mechanism 3 cannot generate elastic deformation, and the resonance frequency of the dual-mass flywheel system is higher. At this time, the vibration frequency generated by the low-speed rotation of the engine is lower than the resonance frequency, so that the resonance of a transmission system such as a dual mass flywheel is not caused. This can reduce or even avoid the generation of a large impact, and is advantageous in extending the life of the dual mass flywheel and its surrounding components.

When the engine rotates at a high speed, for example, above idle speed, the movable element is subjected to a large centrifugal force and moves radially outward to be separated from the fixed element, and at this time, the movable element 5 and the fixed element 4 are elastically connected through the elastic damping mechanism 3, and the elastic damping mechanism 3 can be elastically deformed, which lowers the resonance frequency of the system. Therefore, the vibration frequency generated when the engine rotates at a high rotation speed can be higher than the resonance frequency, and thus the system does not resonate.

Further, when the engine is driven from a high speed to a low speed, the movable member 5 can move inward in the radial direction due to a reduction in the centrifugal force applied thereto until the movable member 5 and the stationary member 4 are recombined. Therefore, the dual-mass flywheel of the technical scheme not only meets the anti-resonance requirement when the engine rotates at a high speed, but also can meet the anti-resonance requirement when the engine rotates at a low rotating speed.

With combined reference to fig. 2, the fixed part 4 may be provided with a plurality of first coupling teeth 40 facing the movable part 5, all the first coupling teeth 40 being arranged along the circumferential direction of the dual mass flywheel; with combined reference to fig. 3, the movable member 5 may be provided with a plurality of second coupling teeth 50 facing the fixed member 4, all the second coupling teeth 50 being arranged in the circumferential direction. The first coupling tooth 40 and the second coupling tooth 50 can engage to couple the movable member 5 and the fixed member 4; the first coupling teeth 40 are separable from the second coupling teeth 50 to separate the movable member 5 and the stationary member 4.

Whether the movable member 5 is movable radially outwards depends on the magnitude of the centrifugal force experienced, which is related to the rotational speed of the engine, and on its own mass. Therefore, the relation between the rotating speed of the engine and the mass of the movable member 5 can be established, and the mass of the movable member 5 is reasonably selected, so that the movable member 5 can not move outwards in the radial direction under the action of corresponding centrifugal force when rotating at the idle speed of the engine and below the idle speed, and is kept meshed with the fixed member 4; meanwhile, when the engine rotates above the idle speed, the movable part 5 can move outwards along the radial direction under the action of a larger centrifugal force to realize the separation from the fixed part 4, and the anti-resonance requirement of the engine at low rotating speed and high rotating speed can be met simultaneously. Meanwhile, the moving speed of the movable member 5 in the separation process or the combination process at different rotating speeds can be adjusted by reasonably selecting the mass of the movable member 5. Here, the idling speed may be used as a threshold value of the engine speed as to whether the movable member 5 moves radially outward, which is merely an example. In other alternatives, the threshold engine speed value may be adjusted for whether the radially outward movement of the movable member 5 has occurred.

Referring to fig. 2 and 3, the first coupling tooth 40 and the second coupling tooth 50 may be involute teeth, in which a single first coupling tooth 40 or second coupling tooth 50 is composed of two symmetrical involute curves. This not only ensures the bonding strength between the movable member 5 and the stationary member 4 to effectively transmit torque, but also makes the contact area of the first engaging teeth 40 and the second engaging teeth 50 small when they are engaged, facilitating the disengagement when the engine exceeds the idling speed.

Referring to fig. 1 to 3, a base 6 may be disposed between the main flywheel 1 and the sub flywheel 2, the base 6 may be fixed to the sub flywheel 2, and the fixing member 4 may be fixed to the main flywheel 1 and pass through the base 6. On at least one side of the base body 6 in the axial direction, a movable member is provided, which may include: movable members, namely a movable member 500 facing the auxiliary flywheel 2 and a movable member 5 facing the main flywheel 1, are arranged on both sides of the base body 6 in the axial direction; alternatively, a movable member is provided on one side of the base in the axial direction. The

movable member

5, 500 is movably connected with the base 6 to realize the radial movement, so as to achieve the purpose of separating and combining the movable member 5 and the fixed member 4. The

movable member

5, 500 is movably connected with the base 6 to move along the radial direction, so that the

movable member

5, 500 is separated from and combined with the fixed member 4. The base body 6 can be used for mounting the

movable members

5, 500, and all the

movable members

5, 500 are integrated in the same base body 6, which not only improves the assembly feasibility of the

movable members

5, 500, but also improves the product compactness.

The base body 6 may be a flange which is coaxially connected to the sub flywheel 2, and the

movable member

5, 500 is disposed on a disk surface of the flange. The elastic damping mechanism 3 comprises two segments of arc-shaped springs 30, and the two segments of arc-shaped springs 30 are limited on the inner wall of the main flywheel 1 through spring guide rails 31. The base 6 has two protruding ends 60 protruding radially outward, two segments of the arc springs 30 may circumferentially surround the base 6, and both ends of each segment of the arc springs 30 are defined by the two protruding ends 60. When the main flywheel 1 and the auxiliary flywheel 2 rotate relatively, the main flywheel 1 and the base body 6 rotate relatively, so that the two sections of arc-shaped springs 30 are compressed and deformed, and the aim of damping is fulfilled.

One side of the base body 6 facing the auxiliary flywheel 2 along the axial direction is provided with a damping fin 8 and a diaphragm spring 9, and the diaphragm spring 9 applies pressure to the damping fin 8, so that the damping fin 8 compresses the movable part 5 and generates damping, the true toxicity amplitude of the dual-mass flywheel is further reduced, and the requirement of resonance prevention is met.

The fixing piece 4 can be a hub penetrating through the flange and the auxiliary flywheel 2 and is connected with the auxiliary flywheel 2 through a bearing, and the bearing can be sleeved on the fixing piece 4 and is accommodated in a central hole of the auxiliary flywheel 2 to be fixedly connected with the auxiliary flywheel 2, so that the main flywheel 1 and the auxiliary flywheel 2 can rotate relatively. Thus, the fixed member 4 comprises a gear wheel having a first coupling tooth 40.

All the movable members are divided into at least one pair, each pair of movable members includes:

movable members

5 and 500 located on both sides of the base 6 in the axial direction and connected together, and the movable member on at least one side in the axial direction has the second coupling tooth 50, which may include: the movable piece 5 on one axial side only is provided with a second combination tooth 50 which can be separated from the fixed piece 4 and combined with the movable piece 5 to drive the movable pieces 500 connected together to move synchronously when moving along the radial direction, or the movable piece on the other axial side only is provided with a second combination tooth; alternatively, the movable members on both sides in the axial direction may have second engaging teeth.

The two

movable members

5, 500 of each pair of movable members are connected together, and the movable member 5 is an active member and can drive the movable members 500 to move synchronously. The two axial sides of the base body 6 are provided with the

movable parts

5 and 500, so that the mass of each pair of movable parts is increased, the position stability of each pair of movable parts when combined can be enhanced, the space of the two axial sides of the base body 6 can be effectively utilized, and the problem that the space utilization rate is low because the volume of the movable part on one side is simply increased for obtaining larger mass is avoided.

The movable part 5 is an active part and can be designed as a sector gear. The movable member 500 may be an arc-shaped disk.

In this solution, the movable member has 4 pairs, arranged circumferentially around the fixed member 4. Furthermore, all the pairs of movable pieces can be uniformly distributed along the circumferential direction, so that the dual-mass flywheel can rotate in a balanced manner, and unnecessary vibration caused by unbalanced centrifugal force when the dual-mass flywheel rotates is avoided. In addition to this, the movable member may have at least two other pairs.

Taking the movable member 5 as an example, the movable connection mode of the movable member 5 and the base 6 may include: one of the base 6 and the movable member 5 is provided with a track hole and the other is provided with a through hole, which may include: the base body 6 is provided with track holes and the movable element 5 with through holes or in addition thereto, the base body is provided with through holes and the movable element with track holes. The base body 6 and the movable member 5 are connected by a pin passing through the track hole and the through hole, the pin being slidable along the track hole wall in the radial direction to move the movable member 5 in the radial direction.

Referring to fig. 4, two track holes are corresponding to each movable element 5, which may mean that at the position of each movable element 5, the base 6 is provided with

track holes

6a and 6b to achieve the purpose of connecting the movable elements 5. In the case where the movable element is provided with two rail holes, two rail holes are provided for each movable element, which means that two rail holes are provided for each movable element.

The rail holes 6a, 6b are arranged along the circumferential direction; from the inside to the outside in the radial direction, the distance between the two

track holes

6a, 6b first decreases and then increases. Referring to fig. 5, the movable member 5 is provided with a through hole, which may be a

linear type hole

5a, 5 b. The movable member 5 may be provided with at least two

linear holes

5a, 5b juxtaposed in the radial direction, the linear holes 5a being further outward than the linear holes 5b in the radial direction, and a direction of linear extension of the

linear holes

5a, 5b may be perpendicular to the radial direction.

Each linear type hole may always overlap with the two

track holes

6a, 6b for the pin to pass through. Therefore, the linear type hole 5a overlaps with the two

track holes

6a and 6b at the same time, so that the two pins 7a pass through the two

track holes

6a and 6b, respectively, after passing through the same linear type hole 5 a; the linear type hole 5b overlaps both the track holes 6a and 6b at the same time so that the two pins 7b pass through the two

track holes

6a and 6b, respectively, after passing through the same linear type hole 5 b. The

pins

7a and 7b are each slidable along the hole wall of the track holes 6a and 6b in the radial direction, and also slidable along the hole wall of the

linear holes

5a and 5b in the longitudinal direction of the

linear holes

5a and 5 b.

During the radially outward movement of the movable member 5, both

pins

7a, 7b move radially outward with the movable member 5. On the one hand, in the coupling position, since the two

track holes

6a and 6b are spaced apart in the circumferential direction, the

pins

7a and 7b on both sides in the circumferential direction contact and rub against the hole walls of the two

track holes

6a and 6b, which restricts the radially outward movement of the movable member 5, so that the movable member 5 cannot easily move radially outward, the coupling stability of the movable member 5 and the fixed member 4 is maintained, and the smooth transmission of torque is ensured. On the other hand, from the joining to the separating process, the two

rail holes

6a, 6b are engaged with the

respective pins

7a, 7b, so that the movable member 5 can be prevented from being freely swung, and the movement stability of the movable member 5 can be ensured. In this regard, in other possible solutions, therefore, at least two track holes corresponding to at least one movable element may be arranged along the circumferential direction. At this time, the track hole may be a linear type extending in the radial direction.

Further, the distance between the two

track holes

6a and 6b is first decreased and then increased, so that an inflection point is formed at a position where the distance between the two

track holes

6a and 6b is minimum. In the coupling position, two pins 7a penetrating through the radially outward linear holes 5a may be disposed at the inflection point, and the two pins 7a receive a relatively large resistance from the hole walls of the two

track holes

6a and 6b in the radially outward direction at the inflection point, which significantly increases the difficulty of the radially outward movement of the movable member 5, and may prevent the movable member 5 from being separated from the stationary member 4 due to the fluctuation of the engine speed, which may cause the damage to the elastic vibration damping mechanism 3 and related parts due to the impact. Therefore, in this case, the coupling stability of the movable member 5 and the fixed member 4 is also better. In other technical solutions, the track hole may be disposed in the movable member, and the linear hole may be disposed in the base member. To achieve the same technical effect, it may be provided that the inflection point is located through the pin which is radially inward.

From coupling to decoupling, as the movable element 5 moves radially outwards, the distance between the two pins 7a passing through the rectilinear holes 5a increases progressively, while the distance between the two pins 7b passing through the rectilinear holes 5b decreases progressively, the two

pins

7a, 7b being able to move not in a direction parallel to said radial direction, but at an angle thereto. The motion tracks of the two

pins

7a and 7b corresponding to the two

linear holes

5a and 5b are different, and the two pins are restricted and limited mutually, so that the motion stability of the movable piece 5 is enhanced.

In the separation position, the linear hole 7b which is radially inward can be positioned at the inflection point, so that the two pins 7b are subjected to larger resistance force of the hole walls of the two

track holes

6a and 6b which is radially inward at the inflection point, and the phenomenon that the movable member 5 and the fixed member 4 are combined by instant misoperation due to overlarge fluctuation of the rotating speed of the engine so as to cause impact can be avoided. In this case, therefore, the movable member 5 has good stability in the disengaged position, ensuring that the elastic damping mechanism 3 can provide stable and continuous damping characteristics. In other technical solutions, the track hole may be disposed in the movable member, and the linear hole may be disposed in the base member. To achieve the same technical effect, it may be provided that the inflection point is located through the pin radially outward.

The track holes 6a and 6b are arc-shaped with variable curvature, the curvature is reduced from inside to outside along the radial direction, and along the circumferential direction, one of the two

track holes

6a and 6b corresponding to each movable piece 5 protrudes towards the other track hole, and the curvature of the salient point is maximum. The track hole 6a protrudes toward the other track hole 6b and the curvature of the convex point is the largest, and the track hole 6b protrudes toward the other track hole 6a and the curvature of the convex point is the largest. The track holes 6a and 6B are arc-shaped, so that the movement tracks of the pins 7a and 7B can be reduced, and the impact caused by instant movement of the movable piece 5 can be avoided. Moreover, the curvature of the arc is changed, so that the convex point of each track hole can be designed to be an arc inflection point, and the

pins

7a and 7b can be smoothly turned when passing through the convex points of the arc track holes 76a and 6b, so that the

pins

7a and 7b are prevented from being cut.

The two

track holes

6a and 6b corresponding to each movable member 5 are symmetrically arranged, for example, a connecting line between the salient point and the salient point can be perpendicular to the radial direction, so that two pins in the same linear hole can be ensured to move uniformly, and the movable member is effectively prevented from shaking in the moving process.

The

movable members

5 and 500 are provided on both sides of the base 6 in the axial direction, the

movable members

5 and 500 are connected together by the

same pins

7a and 7b, and the

pins

7a and 7b penetrate the base 6 and the

movable members

5 and 500 on both sides of the base 6 in the axial direction. In other solutions, the two movable members of each pair may be a single piece.

The track holes 6a and 6b can be formed in the base 6, and the

movable members

5 and 500 on the two sides of the base 6 in the axial direction are provided with the

linear holes

5a and 5b, so that the movable members 5 on the two sides can have the same motion track, and the motion stability can be enhanced. The structure in which the movable member 5 is provided with the

linear holes

5a and 5b can be analogized to the movable member 500.

The above-described technical solutions take the case that the movable member is connected to the auxiliary flywheel and the fixed member is connected to the main flywheel. In other embodiments, the movable member may be connected to the primary flywheel and the stationary member may be connected to the secondary flywheel.

Second embodiment

Referring to fig. 6, the movable element 15 may be provided with an insertion portion 150, and the stationary element 14 may be provided with a receiving portion 14 a;

when the insertion portion 150 is not inserted into the housing portion 14a, the fixed member 14 and the movable member 15 can be separated;

when the insertion portion 150 is inserted into the receiving portion 14a, the stator 14 and the movable element 15 can be coupled.

From the separation to the combination, the fixed element 14 and the movable element 15 rotate relatively, the insertion portion 150 can contact the outer peripheral surface of the movable element 15 first and slide along the outer peripheral surface to fall into the accommodating portion 14a, and then the insertion portion 150 is blocked by the side wall of the accommodating portion 14a, so that the fixed element 14 and the movable element 15 are combined.

The fixed member 14 has an outer circumferential surface facing the movable member 15, and the movable member 15 may have an inner circumferential surface facing the fixed member 14. The insertion portion 150 may be provided on the outer peripheral surface, and the receiving portion 14a may be provided on the inner peripheral surface.

In addition, the movable member may be provided with a receiving groove and the fixed member may be provided with an insertion portion. Thus, one of the movable member and the fixed member is provided with an insertion portion and the other is provided with a receiving portion. Accordingly, one of the insertion portion and the housing portion is provided on the inner peripheral surface of the movable member and the other is provided on the outer peripheral surface of the fixed member.

The receiving portion 14a may be designed as a slot. Alternatively, or in addition, the receiving portion 14a may be an insertion hole.

The receiving portion 14a may extend in an arc shape along the circumferential direction of the dual mass flywheel such that the receiving portion 14a has a substantial circumferential length along the circumferential direction. This circumference increases the effective insertion of the insertion portion 150 into the receiving portion 14a in time when the movable member 15 moves radially inward, thereby enhancing the coupling feasibility of the movable member 15 and the stationary member 14.

Although the present invention is disclosed above, the present invention is not limited thereto. Various changes and modifications may be effected therein by one skilled in the art without departing from the spirit and scope of the invention as defined in the appended claims.

Claims

1. A dual mass flywheel is characterized by comprising a main flywheel and an auxiliary flywheel which are sequentially arranged along the axial direction;

the movable piece and the fixed piece can be combined to enable the main flywheel and the auxiliary flywheel to synchronously rotate; and the number of the first and second groups,

the movable piece can be separated from the fixed piece under the action of gradually increasing centrifugal force along with the increase of the rotating speed of the dual-mass flywheel, so that the main flywheel and the auxiliary flywheel are separated.

2. A twin mass flywheel as defined in claim 1 in which one of said movable member and said fixed member is provided with an insertion portion and the other is provided with a receiving portion;

3. A twin mass flywheel as defined in claim 2 in which said movable member has an inner peripheral surface facing said fixed member, said fixed member has an outer peripheral surface facing said movable member;

one of the insertion portion and the housing portion is provided on the inner peripheral surface and the other is provided on the outer peripheral surface.

4. A twin mass flywheel as defined in claim 2 in which the receiving portion is a slot or socket.

5. The dual mass flywheel of claim 2, wherein the receptacle extends in an arc along a circumferential direction of the dual mass flywheel.

6. A twin mass flywheel as defined in claim 1 in which the fixed member is provided with first engaging teeth facing the movable member, all of the first engaging teeth being arranged in the circumferential direction of the twin mass flywheel;

the movable piece is provided with a plurality of second combination teeth facing the fixed piece, and all the second combination teeth are arranged along the circumferential direction;

the first combining tooth and the second combining tooth can be meshed to combine the movable piece and the fixed piece;

the first combination tooth and the second combination tooth can be separated, so that the movable piece and the fixed piece can be separated.

7. The dual mass flywheel of claim 6 wherein said first and second coupling teeth are involute teeth.

8. A twin mass flywheel as defined in any one of claims 1 to 7 in which a base is provided between the primary flywheel and the secondary flywheel, the base being secured to the secondary flywheel and the fixing member being secured to the primary flywheel and passing through the base;

9. A twin mass flywheel as defined in claim 8 in which the movable members are divided into at least one pair, each pair comprising: the movable pieces are positioned on two sides of the base body along the axial direction and connected together, and the movable pieces on at least one side along the axial direction can be separated from or combined with the fixed pieces.

10. A dual mass flywheel as defined in claim 8 in which said articulation comprises:

one of the base body and the movable piece is provided with a track hole;

11. The dual mass flywheel of claim 10 wherein at least two of said track holes are circumferentially aligned for at least one of said movable members.

12. A twin mass flywheel as defined in claim 10 in which there are two said track holes for each said movable member, arranged circumferentially;

13. A twin mass flywheel as defined in claim 12 in which the orbital aperture is of variable curvature arcuate shape, the curvature increasing and decreasing from inside to outside in the radial direction;

in the circumferential direction, one of the two track holes corresponding to each movable member protrudes toward the other track hole, and the curvature of the convex point is the largest.

14. A twin mass flywheel as defined in claim 13 in which the two track holes for each of the movable members are symmetrically arranged.

15. A twin mass flywheel as defined in claim 12 in which said movable members are provided on both sides of said base in said axial direction, and each of said pins passes through said base and said movable members on both axial sides of said base.

16. A twin mass flywheel as defined in any of claims 1 to 7 in which the movable member has at least two arranged circumferentially around the fixed member.

17. An automobile comprising an engine, a gearbox and a dual mass flywheel as claimed in any one of claims 1 to 16, the dual mass flywheel being connected to the output of the engine via the primary flywheel and to the input of the gearbox via the secondary flywheel.