CN219035459U - Dual-mass flywheel and automobile - Google Patents

Abstract

The utility model discloses a dual-mass flywheel and an automobile, wherein a primary flywheel and a secondary flywheel of the dual-mass flywheel are overlapped along the axial direction, a friction piece is arranged on the periphery of the primary flywheel, a friction disc is arranged on the periphery of the secondary flywheel, the side wall surface of the friction piece is detachably abutted against the periphery of the friction disc, and a vibration reduction part is arranged between the primary flywheel and the secondary flywheel for vibration reduction. When the rotating speed of the dual-mass flywheel is smaller than the preset speed, the friction piece is contacted with the friction disc, the friction moment between the primary flywheel and the secondary flywheel is increased, vibration at low rotating speed is restrained, and as the rotating speed is increased, the friction piece on the primary flywheel is separated from the friction disc on the secondary flywheel, and the friction moment disappears, so that the dual-mass flywheel meets the vibration reduction requirement at high rotating speed. The dual-mass flywheel can inhibit resonance at low engine rotation speed, and further improve the transmission stability and riding comfort of the automobile with the dual-mass flywheel.

Description

Dual-mass flywheel and automobile

Technical Field

The utility model relates to the technical field of automobile parts, in particular to a dual-mass flywheel and an automobile.

Background

The double-mass flywheel can reduce the resonance rotating speed of the transmission system to be out of the common rotating speed range, has obvious vibration reduction effect on the fluctuation of the rotating speed of the engine, brings better NVH performance to the gearbox, and makes the double-mass flywheel technology popular. However, the drive train using the dual mass flywheel still has a resonance speed point in the range of about 300-500rpm, so that part of the vehicle has drive train knocking and whole vehicle shaking when the engine is turned off, and the phenomenon is particularly obvious in the dual-motor hybrid vehicle type. It is found that increasing the hysteresis damping between the primary flywheel and the secondary flywheel has a significant improvement to this phenomenon, but affects the vibration damping effect of the engine in the normal operating speed range. The hysteresis damping of most dual-mass flywheels in the current market is realized by adding plastic parts between a primary flywheel and a secondary flywheel through friction, and the friction force is always constant.

For example, chinese patent document (CN 113236710B) discloses a dual mass flywheel with a particle damping structure, which comprises a primary flywheel and a secondary flywheel, wherein the primary flywheel and the secondary flywheel are connected with each other in torsion and elasticity through at least one spring mechanism, the secondary flywheel comprises a secondary flywheel coaxially connected with the flange, a first particle damping component for damping is arranged along the circumference of the secondary flywheel, and a second particle damping component for damping is arranged along the circumference of the secondary flywheel. However, the friction between the primary flywheel and the secondary flywheel of the dual-mass flywheel is too large to influence the vibration reduction effect of the engine in normal operation, the friction is too small, and the knocking of the drive train and the shaking of the whole vehicle become obvious when the engine is turned on or off, so that the hysteresis damping force of the dual-mass flywheel cannot be considered in full-rotation speed working condition.

Therefore, the damping force brought by the damping component is not adjustable by the dual-mass flywheel in the prior art, so that the vibration reduction effect of the dual-mass flywheel is poor under the working conditions of different rotating speeds.

Disclosure of Invention

The utility model aims to solve the technical problems that the damping force of the dual-mass flywheel brought by the damping component in the prior art is not adjustable, so that the vibration reduction effect of the dual-mass flywheel is poor under the working conditions of different rotating speeds, and the vibration reduction effect of the dual-mass flywheel is influenced.

In order to solve the technical problems, the embodiment of the utility model discloses a dual-mass flywheel, which comprises a primary flywheel, a secondary flywheel and a vibration reduction component, wherein the primary flywheel and the secondary flywheel are overlapped along the axial direction of the dual-mass flywheel, the vibration reduction component is arranged between the primary flywheel and the secondary flywheel, the primary flywheel is used for being connected with a crankshaft of an engine, and the secondary flywheel is used for being connected with a transmission system.

The dual-mass flywheel further comprises at least one friction piece and a friction disc, wherein the friction disc is fixedly arranged on the periphery of the secondary flywheel, the at least one friction piece is arranged on the periphery of the primary flywheel and is positioned on the periphery of the friction disc, one end of each friction piece in the at least one friction piece is rotatably connected to the primary flywheel, and therefore the side wall surface, close to one side of the secondary flywheel, of each friction piece can be detachably abutted against the periphery of the friction disc.

When the primary flywheel is in a static state or the rotating speed of the primary flywheel is smaller than a preset speed, the side wall surface of each friction piece of the at least one friction piece, which is close to one side of the secondary flywheel, is abutted against the periphery of the friction disc; when the rotating speed of the primary flywheel is greater than or equal to the preset speed, each friction piece in at least one friction piece rotates relative to the primary flywheel in the radial direction of the dual-mass flywheel towards the direction away from the friction disc, and the side wall surface of the corresponding friction piece, which is close to one side of the secondary flywheel, is separated from the friction disc.

By adopting the technical scheme, when the dual-mass flywheel is used, the power of the crankshaft is transmitted to the primary flywheel and is transmitted to the secondary flywheel through the vibration reduction component to be subjected to vibration reduction. When the rotating speed of the dual-mass flywheel is smaller than the preset speed, at the moment, the friction piece on the primary flywheel is contacted with the friction disc on the secondary flywheel, a friction force is generated between the friction piece and the friction disc, a large hysteresis damping effect is brought to the space between the primary flywheel and the secondary flywheel, at the moment, the resonance frequency of the dual-mass flywheel is large, the vibration frequency generated by low-rotating-speed rotation of the engine is lower than the resonance frequency, the dual-mass flywheel and the transmission system resonance can be avoided, the vibration reduction effect of the dual-mass flywheel at the low rotating speed is improved, and the problems of knocking of the transmission system and shaking of the whole vehicle generated during starting or flameout of the engine can be well restrained.

And when the rotation speed is increased until the rotation speed is greater than or equal to the preset rotation speed, the friction piece on the primary flywheel is separated from the friction disc on the secondary flywheel, namely, the hysteresis damping between the primary flywheel and the secondary flywheel is disappeared, at the moment, the power on the primary flywheel is transmitted to the secondary flywheel through the damping part, the resonance frequency of the dual-mass flywheel is reduced, the vibration frequency generated when the engine rotates at a high rotation speed is higher than the resonance frequency, and the primary flywheel and the secondary flywheel rotate independently, so that the dual-mass flywheel meets the damping requirement at the high rotation speed.

Therefore, the dual-mass flywheel provided by the utility model can avoid resonance of the dual-mass flywheel under different rotating speeds through the combination and separation between the friction piece and the friction disc, and the vibration reduction requirement of an automobile is met.

The embodiment of the utility model also discloses a dual-mass flywheel which further comprises a connecting disc, wherein the connecting disc is positioned at one side of the secondary flywheel away from the primary flywheel, the inner periphery of the connecting disc is fixedly connected with the secondary flywheel, the friction disc is positioned at the outer periphery of the connecting disc and is fixedly connected with the connecting disc, and the side wall of the friction disc extends along the direction parallel to the axis direction of the dual-mass flywheel.

The friction piece is at least one friction pawl, each friction pawl in the at least one friction pawl is arc-shaped, one end of each friction pawl is provided with a connecting hole, the friction pawl is close to the side wall surface of the secondary flywheel and is provided with a friction surface, and the friction surface is matched with the peripheral side wall surface of the friction disc.

The peripheral edge of the primary flywheel is provided with a connecting shaft corresponding to the connecting hole, and the connecting shaft penetrates through the connecting hole, so that one end of the friction pawl is rotatably connected with the primary flywheel.

The connecting shafts are provided with pre-tightening components, so that the friction surfaces of the friction pawls are pressed against the side wall surfaces of the periphery of the friction disc.

By adopting the technical scheme, the friction pawls on the periphery of the primary flywheel are pressed on the side wall surface of the periphery of the friction disc under the action of the pre-tightening part, friction force is generated between the friction pawls and the side wall surface of the periphery of the friction disc, and the friction disc is connected with the secondary flywheel through the connecting disc, so that the friction force can prevent relative rotation between the primary flywheel and the secondary flywheel, the centrifugal force born by the friction pawls is larger and larger along with the increase of the rotating speed, the pre-tightening force of the pre-tightening part on the side wall surface of the friction pawls and the side wall surface of the friction disc is weakened, the friction force between the friction pawls and the friction disc is reduced, and relative rotation can occur between the primary flywheel and the secondary flywheel. When the rotating speed of the dual-mass flywheel exceeds the preset rotating speed, the centrifugal force applied to the friction pawl is larger than the pretightening force of the pretightening part, the friction pawl is separated from the friction disc, and the power of the primary flywheel is transmitted to the secondary flywheel through the vibration reduction part.

The resonance frequency of the dual-mass flywheel is influenced by the friction force between the friction pawl and the friction disc, the centrifugal force generated during rotation of the dual-mass flywheel is skillfully utilized, the pretightening force of the pretightening component can be counteracted with the centrifugal force, the resonance frequency of the dual-mass flywheel can be reduced along with the increase of the rotating speed, resonance with the vibration frequency of the engine during rotation is avoided, and the vibration reduction effect of the dual-mass flywheel is improved.

The embodiment of the utility model also discloses a dual-mass flywheel, wherein the pre-tightening part is a torsion spring, the torsion spring is provided with a torsion spring main body, a fixing section and a compressing section, the torsion spring main body is in a spiral shape, the fixing section and the compressing section are respectively connected with the torsion spring main body and extend in a staggered manner along the radial direction of the torsion spring main body, and the torsion spring main body is sleeved on the connecting shaft.

The primary flywheel is further provided with a fixing part, the fixing part is located at one side of the connecting shaft away from the friction pawl, the fixing section is abutted to the fixing part, the pressing section is abutted to one end of the friction pawl, and the friction surface of the friction pawl is pressed on the side wall surface of the periphery of the friction disc.

By adopting the technical scheme, the torsion spring is utilized to compress the pretightening force of the friction disc for the friction pawl, and the torsion spring main body is sleeved on the connecting shaft, so that the radial installation space of the dual-mass flywheel is saved. The fixed section butt in fixed part of torsional spring compresses tightly the section butt in the one end of friction pawl, and the torsion of torsional spring makes friction pawl rotate around the connecting axle towards the friction disc, and then the friction surface of friction pawl compresses tightly on the friction disc. And the axial direction of the torsion spring is parallel to the axial direction of the dual-mass flywheel, and the torsion force of the torsion spring is not influenced by the centrifugal force when the dual-mass flywheel rotates.

The embodiment of the utility model also discloses a dual-mass flywheel which comprises a limiting part, wherein the limiting part is fixedly connected to the primary flywheel, the limiting part corresponds to the friction pawl, is positioned at the other end of the friction pawl opposite to one end and is far away from one side of the friction disc.

When the friction pawl rotates around the connecting shaft in a direction away from the friction disc, the friction surface of the friction pawl is separated from the peripheral side wall surface of the friction disc, and the side wall surface, away from the secondary flywheel, of the other end of the friction pawl is abutted to the limiting part.

By adopting the technical scheme, when the dual-mass flywheel is used, the centrifugal force born by the friction pawl is larger and larger along with the higher and higher rotating speed of the dual-mass flywheel, the friction pawl is separated from the friction disc, the friction pawl is unfolded along the circumferential direction of the dual-mass flywheel, the limit part arranged on one side of the friction pawl away from the friction disc can limit the unfolding degree of the friction pawl, the unfolded friction pawl is prevented from colliding with other parts, and the friction pawl can be prevented from occupying the radial space of the excessive dual-mass flywheel after being unfolded under the premise that the friction pawl and the friction disc can be separated.

The embodiment of the utility model also discloses a dual-mass flywheel, wherein at least one friction pawl comprises a first friction pawl, a second friction pawl, a third friction pawl and a fourth friction pawl which are sequentially arranged at intervals along the periphery of the primary flywheel; the connecting shaft is a pin; the limiting part is a limiting column.

By adopting the technical scheme, the four friction pawls arranged at intervals on the periphery of the primary flywheel can uniformly generate friction force along the circumferential direction of the friction disc, so that the primary flywheel and the secondary flywheel are stably connected together at a low rotating speed, and the vibration reduction effect of the dual-mass flywheel at the low rotating speed is ensured.

The embodiment of the utility model also discloses a dual-mass flywheel, wherein two adjacent friction pawls of the first friction pawl, the second friction pawl, the third friction pawl and the fourth friction pawl are arranged in a way that one end of one friction pawl is opposite to the other end of the other friction pawl.

By adopting the technical scheme, the first friction pawl, the second friction pawl, the third friction pawl and the fourth friction pawl are all unfolded along the inertia generated in the rotating direction of the dual-mass flywheel.

The embodiment of the utility model also discloses a dual-mass flywheel, the vibration reduction part comprises a plurality of arc springs, an annular spring guide rail is arranged on the side wall surface of the primary flywheel, which is close to the secondary flywheel, and the arc springs are fixedly arranged on the primary flywheel through the spring guide rail.

The secondary flywheel sets up a plurality of installation department along its circumference outside, and the secondary flywheel passes through the installation department and connects in arc spring to make the secondary flywheel pass through a plurality of arc springs and be connected with the primary flywheel.

By adopting the technical scheme, when the rotating speed of the dual-mass flywheel exceeds the preset rotating speed, the friction pawls are separated from the friction disc, the power of the primary flywheel is transmitted to the secondary flywheel through the plurality of arc springs, the arc springs can weaken torsional vibration in the power transmission process along the circumferential direction of the dual-mass flywheel, the power is transmitted to the secondary flywheel more stably, and then the secondary flywheel outputs the power to a transmission system.

The embodiment of the utility model also discloses a dual-mass flywheel, which further comprises an annular primary flywheel back cover plate, wherein the primary flywheel back cover plate is arranged between the connecting disc and the secondary flywheel and is fixedly connected with the primary flywheel.

By adopting the technical scheme, the arc-shaped spring and the secondary flywheel are arranged in the cavity formed between the primary flywheel and the primary flywheel back cover plate, when the primary flywheel transmits power to the secondary flywheel, the primary flywheel back cover plate can limit the secondary flywheel from moving along the axial direction, and the secondary flywheel is protected. The sealing performance of the dual-mass flywheel is also improved by the rear cover plate of the first-stage flywheel.

The embodiment of the utility model also discloses a dual-mass flywheel, wherein the periphery of the connecting disc is provided with a plurality of connecting claws at intervals along the circumferential direction of the connecting disc, and the connecting claws are used for connecting a gearbox.

By adopting the technical scheme, when the dual-mass flywheel is assembled, the primary flywheel is connected with the crankshaft, the connecting disc is connected to the flange of the output end of the gearbox through the connecting claw, and the plurality of connecting claws arranged at intervals along the circumferential direction of the connecting disc can smoothly transfer the power of the secondary flywheel to the gearbox.

The embodiment of the utility model also discloses an automobile comprising the dual-mass flywheel.

By adopting the technical scheme, the output end of the engine crankshaft of the automobile is assembled on the first-stage flywheel, and the second-stage flywheel of the dual-mass flywheel outputs power to the transmission system. The dual-mass flywheel skillfully utilizes the centrifugal force generated when the dual-mass flywheel rotates, so that a friction piece and a friction disc of the dual-mass flywheel can be separated along with the increase of the rotating speed, and the resonance of the dual-mass flywheel 10 and the superposition of the vibration frequency of an engine are avoided. Therefore, the dual-mass flywheel improves the transmission smoothness of the automobile and also improves the riding experience of passengers in the automobile.

The beneficial effects of the utility model are as follows:

the utility model discloses a dual-mass flywheel, wherein a primary flywheel and a secondary flywheel of the dual-mass flywheel are overlapped along the axial direction of the dual-mass flywheel, a friction piece is arranged on the periphery of the primary flywheel, a friction disk is fixedly arranged on the periphery of the secondary flywheel, the side wall surface of the friction piece, which is close to one side of the secondary flywheel, is detachably abutted against the periphery of the friction disk, and a vibration reduction component is further arranged between the primary flywheel and the secondary flywheel.

When the dual-mass flywheel is used, the power of the crankshaft is transmitted to the primary flywheel and is transmitted to the secondary flywheel through the vibration reduction component to be subjected to vibration reduction. When the rotating speed of the dual-mass flywheel is smaller than a preset speed, at the moment, a friction piece on the primary flywheel is contacted with a friction disc on the secondary flywheel, a friction force is generated between the friction piece and the friction disc, a large hysteresis damping effect is brought to the space between the primary flywheel and the secondary flywheel, at the moment, the primary flywheel and the secondary flywheel rotate integrally, the resonance frequency of the dual-mass flywheel is large, the vibration frequency generated by low-rotating-speed rotation of an engine is lower than the resonance frequency, therefore, the resonance of a transmission system of the dual-mass flywheel is not caused, the vibration reduction effect of the dual-mass flywheel at the low rotating speed is improved, and the problems of knocking of a transmission system and shaking of the whole vehicle generated when the engine is started or extinguished can be well restrained; when the rotation speed is increased until the rotation speed is greater than or equal to the preset rotation speed, the friction piece on the primary flywheel is separated from the friction disc on the secondary flywheel, namely, the hysteresis damping between the primary flywheel and the secondary flywheel is disappeared, at the moment, the power on the primary flywheel is transmitted to the secondary flywheel through the damping part, the resonance frequency of the dual-mass flywheel is reduced, and the vibration frequency generated when the engine rotates at a high rotation speed is higher than the resonance frequency, so that the dual-mass flywheel meets the damping requirement at a high rotation speed.

Furthermore, the utility model also discloses an automobile which is provided with the dual-mass flywheel, and the dual-mass flywheel can slow down the vibration of the transmission system according to different rotating speeds of the automobile, so that the transmission smoothness of the automobile is improved, and the riding experience of passengers in the automobile is also improved.

Drawings

FIG. 1 is an exploded schematic view of a structure of a dual mass flywheel disclosed in an embodiment of the present utility model;

FIG. 2 is an axial cross-sectional view of a dual mass flywheel disclosed in an embodiment of the utility model;

FIG. 3 is a schematic diagram illustrating an assembly of a secondary flywheel of a dual mass flywheel with a friction disk according to an embodiment of the present utility model;

FIG. 4 is a schematic diagram of a dual mass flywheel according to an embodiment of the present utility model at rest or at a rotational speed less than a predetermined rotational speed;

FIG. 5 is a schematic diagram of a dual mass flywheel at a rotational speed greater than or equal to a predetermined rotational speed according to an embodiment of the present utility model;

fig. 6 is a schematic diagram of a side of a primary flywheel facing away from a secondary flywheel of a dual mass flywheel in accordance with an embodiment of the present utility model.

Reference numerals illustrate:

10. a dual mass flywheel;

110. a first-stage flywheel; 111. a connecting shaft; 112. a fixing part;

120. a secondary flywheel; 121. an extension;

130. a vibration damping member; 131. an arc spring;

140. a friction member;

141. a first friction pawl; 142. a second friction pawl; 143. a third friction pawl; 144. a fourth friction pawl;

150. a friction plate;

160. a connecting disc; 161. a connecting claw;

170. a pre-tightening member; 171. a torsion spring;

180. a limit part; 181. a limit column;

190. a first-stage flywheel rear cover plate;

A. the rotation direction of the dual mass flywheel.

Detailed Description

Further advantages and effects of the present utility model will become apparent to those skilled in the art from the disclosure of the present specification, by describing the embodiments of the present utility model with specific examples. While the description of the utility model will be described in connection with the preferred embodiments, it is not intended to limit the inventive features to the implementation. Rather, the purpose of the utility model described in connection with the embodiments is to cover other alternatives or modifications, which may be extended by the claims based on the utility model. The following description contains many specific details for the purpose of providing a thorough understanding of the present utility model. The utility model may be practiced without these specific details. Furthermore, some specific details are omitted from the description in order to avoid obscuring the utility model. It should be noted that, without conflict, the embodiments of the present utility model and features of the embodiments may be combined with each other.

It should be noted that in this specification, like reference numerals and letters denote like items in the following figures, and thus once an item is defined in one figure, no further definition or explanation thereof is necessary in the following figures.

In the description of the present embodiment, it should be noted that the azimuth or positional relationship indicated by the terms "upper", "lower", "inner", "bottom", etc. are based on the azimuth or positional relationship shown in the drawings, or the azimuth or positional relationship in which the inventive product is conventionally put in use, are merely for convenience of describing the present utility model and simplifying the description, and are not indicative or implying that the apparatus or element to be referred to must have a specific azimuth, be configured and operated in a specific azimuth, and therefore should not be construed as limiting the present utility model.

The terms "first," "second," and the like are used merely to distinguish between descriptions and are not to be construed as indicating or implying relative importance.

In the description of the present embodiment, it should also be noted that, unless explicitly specified and limited otherwise, the terms "disposed," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present embodiment can be understood in a specific case by those of ordinary skill in the art.

For the purpose of making the objects, technical solutions and advantages of the present utility model more apparent, embodiments of the present utility model will be described in further detail below with reference to the accompanying drawings.

The embodiment of the utility model discloses a dual mass flywheel, as shown in fig. 1 and 2, the dual mass flywheel 10 comprises a primary flywheel 110, a secondary flywheel 120 and a vibration reduction component 130, wherein the primary flywheel 110 and the secondary flywheel 120 are overlapped along the axial direction of the dual mass flywheel 10, the vibration reduction component 130 is arranged between the primary flywheel 110 and the secondary flywheel 120, the primary flywheel 110 is used for being connected with a crankshaft of an engine, and the secondary flywheel 120 is used for being connected with a transmission system.

Specifically, the dual mass flywheel 10 further includes at least one friction member 140 and a friction disc 150, the friction disc 150 is fixedly disposed on the outer periphery of the secondary flywheel 120, at least one friction member 140 is disposed on the outer periphery of the primary flywheel 110 and is located on the outer periphery of the friction disc 150, and one end of each friction member 140 in the at least one friction member 140 is rotatably connected to the primary flywheel 110, so that a side wall surface of each friction member 140, which is close to one side of the secondary flywheel 120, can be detachably abutted against the outer periphery of the friction disc 150.

More specifically, when the primary flywheel 110 is in a stationary state or the rotational speed of the primary flywheel 110 is less than a predetermined speed, the side wall surface of each friction member 140 of the at least one friction member 140 on the side closer to the secondary flywheel 120 abuts against the outer periphery of the friction plate 150. When the rotational speed of the primary flywheel 110 is greater than or equal to the predetermined speed, each friction member 140 of the at least one friction member 140 rotates in a direction away from the friction plate 150 in the radial direction of the dual mass flywheel 10 with respect to the primary flywheel 110, and the side wall surface of the corresponding friction member 140 on the side close to the secondary flywheel 120 is separated from the friction plate 150.

More specifically, when the dual-mass flywheel 10 is assembled, the friction member 140 is disposed on the outer periphery of the primary flywheel 110, and the friction plate 150 is disposed on the outer periphery of the secondary flywheel 120, so that the dual-mass flywheel 10 does not occupy the axial space of the dual-mass flywheel 10, thereby facilitating the arrangement of the dual-mass flywheel 10 in the transmission system.

More specifically, in use, the dual mass flywheel 10 is driven by the crankshaft power to the primary flywheel 110 and through the damping member 130 to the secondary flywheel 120 for damping. As shown in fig. 4, when the rotation speed of the dual-mass flywheel 10 is less than the predetermined speed, at this time, the friction member 140 on the primary flywheel 110 contacts the friction disc 150 on the secondary flywheel 120, a friction force is generated between the friction member and the friction disc, so that a larger hysteresis damping effect is brought between the primary flywheel 110 and the secondary flywheel 120, the resonance frequency of the dual-mass flywheel 10 is larger, and the vibration frequency generated by the low rotation speed rotation of the engine is lower than the resonance frequency, so that the resonance of the transmission system of the dual-mass flywheel 10 is not caused, the vibration reduction effect of the dual-mass flywheel 10 at the low rotation speed is improved, and the problems of knocking of the transmission system and shaking of the whole vehicle generated during the starting or the extinction of the engine can be well restrained; as shown in fig. 5, as the rotational speed increases until it is greater than or equal to the predetermined rotational speed, the friction member 140 on the primary flywheel 110 is separated from the friction disc 150 on the secondary flywheel 120, that is, the hysteresis damping between the primary flywheel 110 and the secondary flywheel 120 disappears, at this time, the power on the primary flywheel 110 is transmitted to the secondary flywheel 120 through the vibration damping member 130, the resonance frequency of the dual-mass flywheel 10 is reduced, the vibration frequency generated when the engine rotates at a high rotational speed is higher than the resonance frequency, and the primary flywheel 110 and the secondary flywheel 120 rotate independently, so that the dual-mass flywheel 10 satisfies the vibration damping requirement at a high rotational speed. The dual-mass flywheel 10 avoids resonance of the dual-mass flywheel 10 at different rotation speeds through the combination and separation between the friction piece 140 and the friction disk 150, and can meet the vibration reduction requirement of an automobile.

More specifically, as shown in fig. 6, the primary flywheel 110 is provided with a connecting hole, an output shaft of the crankshaft can be connected to the primary flywheel 110 in an interference fit manner, the primary flywheel 110 transmits rotational torque of the transmission engine, and the secondary flywheel 120 is connected with an output flange of the gearbox for improving rotational inertia of the gearbox.

More specifically, the predetermined rotational speed may be set to a rotational speed of the engine at idle speed in a range of 800 rpm to 2000 rpm, and may specifically be 800 rpm, 900 rpm, 1000 rpm, 1500 rpm or 2000 rpm, which may be selected by those skilled in the art according to the output characteristics of the engine, and the embodiment is not particularly limited.

More specifically, the torque of the primary flywheel 110 can be transmitted to the secondary flywheel 120 through the vibration reduction member 130, and the friction between the friction member 140 and the friction plate 150 only serves to limit the relative rotation therebetween; when the rotational speed of the dual mass flywheel 10 is lower than the predetermined rotational speed, the torque of the primary flywheel 110 can also be transmitted to the friction plate 150 of the secondary flywheel 120 through the friction member 140, and both rotate as a whole. Those skilled in the art can design to improve the vibration damping effect of the dual mass flywheel 10 according to practical situations and specific requirements, and the present embodiment is not limited thereto.

More specifically, the friction member 140 may be configured as a plurality of friction pawls spaced along the outer circumference of the primary flywheel 110, and the plurality of friction pawls are pressed against the outer circumference of the friction disk 150 by the pre-tightening member 170, limiting the relative movement between the primary flywheel 110 and the secondary flywheel 120. The friction pawls may be provided 1, 2, 3, 4 or 6 in the circumferential direction of the primary flywheel 110, and preferably in this embodiment, the friction pawls are provided 4 in the circumferential direction of the primary flywheel 110 at an interval of 90 °. Those skilled in the art may design according to practical situations and specific requirements, and the embodiment is not limited thereto.

In another embodiment, the friction member 140 may be a ring-shaped friction ring that is movable in the circumferential direction, and the tightening member is disposed on the outer side of the friction ring and is capable of tightening the friction ring in the circumferential direction of the friction ring, such that the inner wall surface of the friction ring abuts against the inner wall surface of the friction disk 150.

Further, the embodiment of the present utility model also discloses a dual mass flywheel, as shown in fig. 1-3, the dual mass flywheel 10 further comprises a connection disc 160, the connection disc 160 is located at one side of the secondary flywheel 120 far from the primary flywheel 110, the inner circumference of the connection disc 160 is fixedly connected with the secondary flywheel 120, the friction disc 150 is located at the outer circumference of the connection disc 160 and is fixedly connected with the connection disc 160, and the side wall of the friction disc 150 extends along the direction parallel to the axial direction of the dual mass flywheel 10.

Specifically, the at least one friction member 140 is at least one friction pawl, each friction pawl in the at least one friction pawl is arc-shaped, one end of the friction pawl is provided with a connecting hole, the friction pawl is close to the side wall surface of the secondary flywheel 120 and is provided with a friction surface, and the friction surface is matched with the peripheral side wall surface of the friction disc 150.

More specifically, the outer peripheral edge of the primary flywheel 110 is provided with a connection shaft 111 corresponding to the connection hole, and the connection shaft 111 is inserted through the connection hole, so that one end of the friction pawl is rotatably connected to the primary flywheel 110.

More specifically, the coupling shafts 111 are provided with a pre-tightening member 170 so that the friction surfaces of the friction pawls are pressed against the side wall surfaces of the outer periphery of the friction plate 150.

More specifically, the friction pawls on the outer periphery of the primary flywheel 110 are pressed against the side wall surface on the outer periphery of the friction disc 150 by the pre-tightening member 170, so that friction force is generated between the friction pawls and the side wall surface on the outer periphery of the friction disc 150, and the friction disc 150 is connected with the secondary flywheel 120 through the connecting disc 160, so that the friction force can prevent relative rotation between the primary flywheel 110 and the secondary flywheel 120, as the rotational speed increases, the centrifugal force applied to the friction pawls is larger and larger, the pre-tightening force applied to the friction pawls by the pre-tightening member 170 and the side wall surface of the friction disc 150 is weakened, the friction force between the friction pawls and the friction disc 150 is reduced, and relative rotation can occur between the primary flywheel 110 and the secondary flywheel 120. When the rotational speed of the dual mass flywheel 10 exceeds the predetermined rotational speed, the centrifugal force applied to the friction pawls is greater than the pre-tightening force of the pre-tightening member 170, the friction pawls are separated from the friction plate 150, and the power of the primary flywheel 110 is transmitted to the secondary flywheel 120 through the vibration reduction member 130. The resonance frequency of the dual-mass flywheel 10 is affected by the friction force between the friction pawls and the friction disc 150, and the centrifugal force generated during the rotation of the dual-mass flywheel 10 is skillfully utilized, so that the pretightening force of the pretightening member 170 can be counteracted with the centrifugal force, and the resonance frequency of the dual-mass flywheel 10 can be reduced along with the increase of the rotating speed, thereby avoiding resonance consistent with the vibration frequency during the rotation of the engine, and improving the vibration reduction effect of the dual-mass flywheel 10.

In such an embodiment, the pre-tightening member 170 may employ a torsion spring 171, and the torsion spring 171 is disposed at the junction of the friction pawl and the primary flywheel 110 such that the friction pawl rotates around the junction toward the outer circumference of the friction disk 150 and compresses.

In another embodiment, the pre-tightening part 170 may also be provided as a solenoid valve arranged in a radial direction, the output end of which pushes the friction pawls towards the friction disc 150 when the rotational speed of the dual mass flywheel 10 is below a predetermined rotational speed.

More specifically, the connection disc 160 and the secondary flywheel 120 may be connected by a bolt, a clamping connection, and a riveting connection, and preferably, in this embodiment, a plurality of connection holes are formed on an inner edge of the connection disc 160 along a circumferential direction, and corresponding round holes are formed on an inner edge of the secondary flywheel 120, so that the two are fixedly connected by the bolt. Those skilled in the art may design according to practical situations and specific requirements, and the embodiment is not limited thereto.

More specifically, the friction surface of the friction pawl is provided with a coating made of friction material to increase the friction force between the friction pawl and the friction disk 150, and further to increase the wear resistance of the friction pawl and the friction disk. The friction material includes asbestos resin type friction material, asbestos-free resin type friction material, metal fiber reinforced friction material, semi-metal fiber reinforced friction material, hybrid fiber reinforced friction material, etc., which are commonly used in the art, and the embodiment is not particularly limited thereto.

Still further, the embodiment of the present utility model further discloses a dual-mass flywheel, wherein the pre-tightening member 170 is a torsion spring 171, the torsion spring has a torsion spring main body, a fixing section and a compressing section, the torsion spring main body is in a spiral shape, the fixing section and the compressing section are respectively connected to the torsion spring main body and extend in a staggered manner along the radial direction of the torsion spring main body, and the torsion spring main body is sleeved on the connecting shaft 111.

Specifically, the primary flywheel 110 is further provided with a fixing portion 112, the fixing portion 112 is located at one side of the connecting shaft 111 away from the friction pawl, the fixing section is abutted to the fixing portion 112, the pressing section is abutted to one end of the friction pawl, and the friction surface of the friction pawl is pressed against the side wall surface of the outer periphery of the friction disc 150.

More specifically, a bar-shaped hole is provided at one end of the friction pawl, the bar-shaped hole corresponds to the pressing section of the torsion spring 171, and the pressing section of the torsion spring 171 is pressed against the inner wall surface of the bar-shaped hole of the friction pawl.

More specifically, the torsion spring 171 is utilized to compress the friction disc 150 by the pretightening force of the friction pawl, and the torsion spring body is sleeved on the connecting shaft 111, so that the radial installation space of the dual-mass flywheel 10 is saved. The fixed section of the torsion spring 171 is abutted to the fixed portion 112, the pressing section is abutted to one end of the friction pawl, the torsion force of the torsion spring 171 enables the friction pawl to rotate around the connecting shaft 111 towards the friction disc 150, and then the friction surface of the friction pawl is pressed on the friction disc 150. And the axial direction of the torsion spring 171 is parallel to the axial direction of the dual-mass flywheel 10, the torsion force of the torsion spring 171 is not affected by the centrifugal force when the dual-mass flywheel 10 rotates.

Still further, the embodiment of the present utility model further discloses a dual-mass flywheel, as shown in fig. 1, the dual-mass flywheel 10 includes a limiting portion 180, the limiting portion 180 is fixedly connected to the primary flywheel 110, and the limiting portion 180 corresponds to the friction pawl, is located at the other end of the friction pawl opposite to one end and is far away from one side of the friction disc 150.

Specifically, when the friction pawl rotates about the connection shaft 111 in a direction away from the friction disk 150, the friction surface of the friction pawl is separated from the outer peripheral side wall surface of the friction disk 150, and the side wall surface of the other end of the friction pawl, which is away from the secondary flywheel 120, abuts against the stopper 180.

More specifically, when the dual-mass flywheel 10 is in use, as the rotational speed of the dual-mass flywheel 10 is higher and higher, the centrifugal force applied to the friction pawls is larger and larger, so that the friction pawls are separated from the friction disc 150, and are unfolded along the circumferential direction of the dual-mass flywheel 10, and the limit part 180 arranged on one side of the friction pawls far away from the friction disc 150 can limit the unfolding degree of the friction pawls, so that the unfolded friction pawls are prevented from colliding with other components; moreover, on the premise of ensuring that the friction pawls and the friction disc 150 can be separated, the friction pawls do not occupy too much radial space of the dual-mass flywheel 10 after being unfolded.

Still further, an embodiment of the present utility model further discloses a dual mass flywheel, as shown in fig. 1 to 6, at least one friction pawl includes a first friction pawl 141, a second friction pawl 142, a third friction pawl 143 and a fourth friction pawl 144 which are spaced along the outer circumference of the primary flywheel 110, and the connecting shaft 111 is a pin; the limit portion 180 is a limit post 181.

Specifically, the four friction pawls disposed at intervals on the outer periphery of the primary flywheel 110 can uniformly generate friction along the circumferential direction of the friction disk 150, so that the primary flywheel 110 and the secondary flywheel 120 are stably connected together at a low rotation speed, and the vibration reduction effect of the dual-mass flywheel 10 at the low rotation speed is ensured.

More specifically, 4 mounting plates are disposed at intervals on the outer periphery of the primary flywheel 110, the mounting plates correspond to the positions of the friction pawls, and the pin posts and the limit posts 181 are disposed on the corresponding mounting plates.

Still further, the embodiment of the present utility model also discloses a dual mass flywheel, as shown in fig. 4 and 5, two adjacent friction pawls among the first friction pawl 141, the second friction pawl 142, the third friction pawl 143 and the fourth friction pawl 144, wherein one end of one friction pawl is disposed opposite to the other end of the other friction pawl.

Specifically, the dual mass flywheel 10 can rotate in the clockwise direction shown in fig. 4 a, that is, the output rotation direction of the engine, and the first friction pawl 141, the second friction pawl 142, the third friction pawl 143, and the fourth friction pawl 144 can be deployed by inertia generated in the rotation direction of the dual mass flywheel 10.

Still further, the embodiment of the present utility model also discloses a dual-mass flywheel, as shown in fig. 1, the vibration damping component 130 includes a plurality of arc springs 131, the side wall surface of the primary flywheel 110, which is close to the secondary flywheel 120, is provided with an annular spring guide rail, and the plurality of arc springs 131 are fixedly arranged on the primary flywheel 110 through the spring guide rail.

Specifically, the secondary flywheel 120 is provided with a plurality of mounting portions along a circumferential outer side thereof, and the secondary flywheel 120 is connected to the arc springs 131 through the mounting portions, so that the secondary flywheel 120 is connected to the primary flywheel 110 through the plurality of arc springs 131.

More specifically, when the rotational speed of the dual mass flywheel 10 exceeds a predetermined rotational speed, the friction pawls are separated from the friction discs 150, the power of the primary flywheel 110 is transmitted to the secondary flywheel 120 through the plurality of arc springs 131, and the arc springs 131 can attenuate torsional vibration during power transmission in the circumferential direction of the dual mass flywheel 10, more smoothly transmit the power to the secondary flywheel 120, and then the secondary flywheel 120 outputs the power to the transmission system.

More specifically, the arc springs 131 may be arranged 2, 3 or 4 at intervals along the circumferential direction of the primary flywheel 110, and preferably, in this embodiment, the arc springs 131 are arranged 2. Two extension parts 121 are arranged on the periphery of the secondary flywheel 120, the two extension parts 121 correspond to the arc springs 131, and the secondary flywheel 120 is connected with the arc springs 131 through the connection of the extension parts 121. The secondary flywheel 120 may also be welded to the ends of the arcuate springs 131. Those skilled in the art may design according to practical situations and specific requirements, and the embodiment is not limited thereto.

Still further, the embodiment of the present utility model also discloses a dual-mass flywheel, as shown in fig. 1 and 2, the dual-mass flywheel 10 further comprises an annular primary flywheel back cover plate 190, wherein the primary flywheel back cover plate 190 is disposed between the connection plate 160 and the secondary flywheel 120, and is fixedly connected with the primary flywheel 110.

Specifically, the arc spring 131 and the secondary flywheel 120 are installed in a cavity formed between the primary flywheel 110 and the primary flywheel rear cover plate 190, and when the primary flywheel 110 transmits power to the secondary flywheel 120, the primary flywheel rear cover plate 190 can limit the secondary flywheel 120 from moving in the axial direction and protect the secondary flywheel 120. The primary flywheel back cover plate 190 also improves the sealing of such a dual mass flywheel 10.

More specifically, the primary flywheel 110 and the primary flywheel back cover plate 190 may be connected by crimping, bolting, welding or riveting, which is not specifically limited in this embodiment.

More specifically, lubricating oil can be injected into the cavity formed by the primary flywheel 110 and the primary flywheel rear cover plate 190, so that the contact part of the arc-shaped spring 131 and the primary flywheel 110 can be lubricated, and the service life of the device is prolonged.

Still further, an embodiment of the present utility model also discloses a dual mass flywheel, as shown in fig. 1 to 3, the outer circumference of the connection disc 160 is provided with a plurality of connection claws 161 at intervals along the circumference thereof, and the plurality of connection claws 161 are used to connect a transmission.

Specifically, in the dual mass flywheel 10, when assembled, the primary flywheel 110 is connected to the crankshaft, the connection plate 160 is connected to the flange of the output end of the transmission through the connection claw 161, and the plurality of connection claws 161 arranged at intervals along the circumferential direction of the connection plate 160 can smoothly transmit the power of the secondary flywheel 120 to the transmission.

More specifically, the connection claws 161 are arranged 2, 3 or 4 in the circumferential direction of the connection pad 160, and preferably, in the present embodiment, the connection claws 161 are arranged at intervals of 3 in the circumferential direction of the connection pad 160 at an interval angle of 120 °. Those skilled in the art may design according to practical situations and specific requirements, and the embodiment is not limited thereto.

Embodiments of the present utility model also disclose an automobile comprising a dual mass flywheel 10 of any of the above.

Specifically, the output end of the engine crankshaft of such an automobile is mounted on the primary flywheel 110, and the secondary flywheel 120 of the dual mass flywheel 10 outputs power to the transmission system. The dual-mass flywheel 10 skillfully utilizes the centrifugal force generated when the dual-mass flywheel 10 rotates, so that the friction piece 140 and the friction disk 150 of the dual-mass flywheel 10 can be separated along with the increase of the rotating speed, and the resonance frequency of the dual-mass flywheel 10 and the vibration frequency of an engine are prevented from coinciding and resonating. Therefore, the dual-mass flywheel improves the transmission smoothness of the automobile and also improves the riding experience of passengers in the automobile.

While the utility model has been shown and described with reference to certain preferred embodiments thereof, it will be understood by those skilled in the art that the foregoing is a further detailed description of the utility model with reference to specific embodiments, and it is not intended to limit the practice of the utility model to those descriptions. Various changes in form and detail may be made therein by those skilled in the art, including a few simple inferences or alternatives, without departing from the spirit and scope of the present utility model.

Claims (10)

1. The utility model provides a dual mass flywheel, dual mass flywheel includes one-level flywheel, second grade flywheel and damping part, one-level flywheel with the second grade flywheel is followed dual mass flywheel's axis direction stacks, damping part sets up one-level flywheel with between the second grade flywheel, one-level flywheel is used for being connected with the bent axle of engine, the second grade flywheel is used for being connected with transmission system, its characterized in that:

the dual-mass flywheel further comprises at least one friction piece and a friction disc, wherein the friction disc is fixedly arranged on the periphery of the secondary flywheel, the at least one friction piece is arranged on the periphery of the primary flywheel and is positioned outside the periphery of the friction disc, and one end of each friction piece in the at least one friction piece is rotatably connected with the primary flywheel so that the side wall surface of each friction piece, which is close to one side of the secondary flywheel, can be detachably abutted against the periphery of the friction disc; wherein the method comprises the steps of

When the primary flywheel is in a static state or the rotating speed of the primary flywheel is smaller than a preset speed, the side wall surface of each friction piece of the at least one friction piece, which is close to one side of the secondary flywheel, is abutted against the periphery of the friction disc;

when the rotating speed of the primary flywheel is greater than or equal to a preset speed, each friction piece in the at least one friction piece rotates relative to the primary flywheel in the radial direction of the dual-mass flywheel in the direction away from the friction disc, and the corresponding side wall surface of the friction piece, which is close to one side of the secondary flywheel, is separated from the friction disc.

2. A dual mass flywheel as defined in claim 1, wherein:

the dual-mass flywheel further comprises a connecting disc, the connecting disc is positioned at one side of the secondary flywheel away from the primary flywheel, the inner periphery of the connecting disc is fixedly connected with the secondary flywheel, the friction disc is positioned at the outer periphery of the connecting disc and is fixedly connected with the connecting disc, and the side wall of the friction disc extends along the direction parallel to the axis direction of the dual-mass flywheel;

the friction piece is at least one friction pawl, each friction pawl in the at least one friction pawl is arc-shaped, one end of each friction pawl is provided with a connecting hole, a friction surface is arranged on the side wall surface, close to the secondary flywheel, of each friction pawl, and the friction surface is matched with the peripheral side wall surface of the friction disc;

the outer peripheral edge of the primary flywheel is provided with a connecting shaft corresponding to the connecting hole, and the connecting shaft penetrates through the connecting hole, so that one end of the friction pawl is rotatably connected with the primary flywheel;

a pre-tightening part is arranged on each connecting shaft, so that the friction surface of the friction pawl is pressed against the side wall surface of the periphery of the friction disc.

3. A dual mass flywheel as defined in claim 2, wherein:

the pre-tightening component is a torsion spring, the torsion spring is provided with a torsion spring main body, a fixing section and a compressing section, the torsion spring main body is spiral, the fixing section and the compressing section are respectively connected with the torsion spring main body and extend in a staggered manner along the radial direction of the torsion spring main body, and the torsion spring main body is sleeved on the connecting shaft;

the primary flywheel is further provided with a fixing part, the fixing part is located at one side, far away from the friction pawls, of the connecting shaft, the fixing section is abutted to the fixing part, the pressing section is abutted to one end of the friction pawls, and the friction surface of the friction pawls is pressed on the side wall surface of the periphery of the friction disc.

4. A dual mass flywheel as defined in claim 2, wherein:

the dual-mass flywheel comprises a limiting part which is fixedly connected with the primary flywheel, corresponds to the friction pawl, is positioned at the other end of the friction pawl opposite to the one end and is far away from one side of the friction disc;

when the friction pawl rotates around the connecting shaft in a direction away from the friction disc, the friction surface of the friction pawl is separated from the peripheral side wall surface of the friction disc, and the side wall surface, which is away from the secondary flywheel, of the other end of the friction pawl is abutted to the limiting part.

5. The dual mass flywheel of claim 4, wherein:

the at least one friction pawl comprises a first friction pawl, a second friction pawl, a third friction pawl and a fourth friction pawl which are sequentially arranged at intervals along the periphery of the primary flywheel;

the connecting shaft is a pin;

the limiting part is a limiting column.

6. The dual mass flywheel of claim 5, wherein in any adjacent two of the first friction pawl, the second friction pawl, the third friction pawl and the fourth friction pawl, the one end of one of the friction pawls is disposed opposite the other end of the other friction pawl.

7. A dual mass flywheel as claimed in any one of claims 2 to 6, wherein:

the vibration reduction component comprises a plurality of arc springs, an annular spring guide rail is arranged on the side wall surface, close to the secondary flywheel, of the primary flywheel, and the arc springs are fixedly arranged on the primary flywheel through the spring guide rail;

the secondary flywheel sets up a plurality of installation department along its circumference outside, the secondary flywheel pass through installation department connect in arc spring, so that the secondary flywheel pass through a plurality of arc springs with the primary flywheel is connected.

8. The dual mass flywheel of claim 7, wherein:

the dual-mass flywheel further comprises an annular first-stage flywheel rear cover plate, wherein the first-stage flywheel rear cover plate is arranged between the connecting disc and the second-stage flywheel and fixedly connected with the first-stage flywheel.

9. The dual mass flywheel of claim 7, wherein:

the periphery of connection pad is provided with a plurality of connection jack catch along its circumference interval, a plurality of connection jack catch are used for connecting the gearbox.

10. An automobile comprising a dual mass flywheel as claimed in any one of claims 1 to 9.

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