阅读说明：本技术 阻尼设备 (Damping device ) 是由 D.弗尼乌克斯 于 2020-03-23 设计创作，主要内容包括：本发明涉及一种阻尼设备(1),其包括主质体(2)、副质体(3)以及布置在质体之间的蓄能器、连接至主质体的第一摩擦元件(5)和相对于第一摩擦元件旋转并压靠在主质体上第二摩擦元件(6)以及锁定部件(10),所述锁定部件连接至副质体,在离心力的作用下可动,并且在预定的转速值以下刚性地连接至第二摩擦元件,所述锁定部件形成板簧(13),所述板簧构造成使得板簧的自由端(24)定位成在休止时沿着周向压靠在由第二摩擦元件形成的止挡部(14)上,并且能够在离心力的作用下从止挡部移动离开。(The invention relates to a damping device (1) comprising a main mass (2), a secondary mass (3) and an energy accumulator arranged between the masses, a first friction element (5) connected to the main mass, and a second friction element (6) rotating relative to the first friction element and pressing against the main mass, and a locking member (10) connected to the secondary mass, movable under the action of centrifugal force and rigidly connected to the second friction element below a predetermined rotational speed value, said locking member forming a leaf spring (13) configured such that a free end (24) of the leaf spring is positioned to press circumferentially against a stop (14) formed by the second friction element at rest and can move away from the stop under the action of centrifugal force.)

1. A damping device (1) for absorbing or compensating rotational vibrations, the damping device comprising:

a main inertia mass (2),

a secondary inertia mass (3), and

an accumulator arranged between the primary and secondary inertia masses, the primary and secondary inertia masses being capable of relative rotation against the action of the accumulator,

at least one first friction element (5) rigidly connected to the main inertia mass for rotation therewith, and at least one second friction element (6) rotating with respect to the first friction element and pressing against the main inertia mass, and

a locking member (10) rigidly connected to the secondary inertia mass for rotation therewith, movable under the action of centrifugal force and rigidly connected to the second friction element when the rotation speed of the engine is lower than a predetermined value,

the locking means form at least one leaf spring (13) configured such that its free end (24) is positioned, at rest, circumferentially against a stop (14) formed by the second friction element and can be moved away from the stop under the effect of centrifugal force, thereby releasing the second friction element.

2. A damping device according to claim 1, wherein the second friction element forms a ring having a radial dimension that varies along the circumferential travel, the ring extending between a substantially circular inner profile (16) and an outer profile (17) having a variable radial position, a portion of which forms the stop.

3. A damping device according to claim 2, wherein the free end has a substantially flat shape able to follow a similar corresponding shape formed by the outer contour of the ring.

4. A damping device according to one of claims 1-3, wherein the stop forms a first surface (15) extending radially from a circle with a first radius to an apex with a second, larger radius, which first surface at its apex extends by a second surface (18) extending along the circumference, which second surface extends by a third surface (19) extending along a ramp to the circle with the first radius, the free end of the leaf spring being positioned facing the third surface.

5. The damping device according to one of claims 1 to 4, wherein the second friction element has a plurality of stops.

6. The damping device of claim 5, wherein the locking component comprises a number of leaf springs equal to half the number of stops.

7. The damping device according to one of claims 5 and 6, wherein the locking member comprises a series of first and second leaf springs arranged in sequence, the free ends of each of the two leaf springs being arranged end to end or in sequence.

8. The damping device according to one of claims 1 to 7, wherein the locking part forms: an annular first portion (11) rigidly connected to the secondary mass for rotation therewith; and a second part (12) comprising a fixed part and a movable part, the free end of the leaf spring being formed by the movable part while extending inside a cylindrical surface formed by the fixed part at rest.

9. The damping apparatus of claim 8, wherein the first portion and the second portion extend substantially perpendicular to each other.

10. The damping device according to one of claims 1 to 9, wherein the free end of the leaf spring is displaceable radially outwards until it is pressed against the secondary mass.

11. The damping apparatus according to one of claims 1 to 10, characterized in that the free end of the leaf spring is configured such that it moves away from the stop of the second friction element at rotational speeds between 400 and 600 rpm.

12. Method for manufacturing a locking member of a damping device according to one of the preceding claims, characterized in that it comprises the following steps:

the metal plate is cut out, and then,

bending the metal sheet around its peripheral edge to obtain a first portion (25) and a second portion (26) comprising a leaf spring, and then

The leaf spring is bent such that its free end is located within the cylinder defined by the remainder of the second portion.

Technical Field

The present invention relates to a damping device, in particular for a motor vehicle.

Background

Damping devices are known, such as those described in patent application FR 2553848, which comprise a primary inertial mass and a secondary inertial mass. The primary inertia mass can be connected to the internal combustion engine. The secondary inertia mass can be connected to the input portion of the gearbox. The primary and secondary masses are capable of limited rotation relative to each other. The damping provided between the two inertia masses rotating relative to one another is formed by an energy accumulator, for example a helical compression spring, arranged between the primary and secondary inertia masses.

A rigid stop is provided between the two inertia masses to prevent over-compression of the accumulator in the event of large oscillation amplitudes of the two inertia masses after excitation between the two inertia masses.

In order to damp or prevent vibrations, i.e. to damp or prevent the impact of the stop, damping is also provided by a friction device acting in parallel with the energy accumulator.

A friction device such as that described in patent application FR 2553848 is formed by three first friction rings rotatably connectable to the primary inertia mass and three second friction rings rotatably connected to the secondary inertia mass. The third friction ring is placed between one of the first friction rings and the secondary inertia mass. The spring ring is placed between the primary inertia mass and the other first friction ring so that the respective friction rings exert an axial force with respect to each other and the third friction ring exerts an axial force with respect to the primary inertia mass. The first friction ring can be rotatably connected to a locking member formed by a leaf spring rotatably fixed to the primary inertia mass and by cooperating teeth mounted on the free end of the leaf spring. These mating teeth are capable of engaging with complementary teeth formed on each first friction ring. This engagement makes it possible to maintain the rotational connection of the first friction ring with the main inertia mass.

Engagement is maintained as long as the speed of the engine is below the speed threshold. Below this threshold value and when the engine is running, the primary and secondary masses rotate relative to each other with a degree of resistance resulting from the friction of the respective friction rings relative to each other and from the friction of the third friction ring against the secondary mass. Above the speed threshold, the leaf spring tends to be lifted relative to the first friction ring. This then makes possible frictionless displacement between the primary and secondary inertia masses. The connection between the first friction ring and the main inertia mass no longer exists. As a result, friction between the third friction ring and the second mass no longer occurs.

The friction device thus makes it possible to generate the hysteresis necessary to generate the resistance between the two inertia masses, said resistance decreasing as the rotation speed increases. This arrangement ensures that the resistance to rotation is relatively high at low angular displacements and increases with the relative rotation of the inertia masses, so that the occurrence of oscillations between the two inertia masses is eliminated as the rotational speed increases.

Thus, it will be appreciated that such a friction device is necessary to start the engine. However, if a high level of friction is required for starting, the friction device may be cumbersome to operate. In addition, such friction devices must not be too large or too heavy, otherwise they are complicated to operate.

The presence of the mating teeth and the presence of a large number of friction rings increases the weight of such devices. In addition, a reliable and reproducible restoration of the rigid connection cannot be ensured by this engagement.

Disclosure of Invention

The present invention aims to overcome these drawbacks and provides a damping device for absorbing or compensating rotational vibrations, comprising:

the mass of the main inertia mass is,

a secondary inertia mass, and

an accumulator arranged between the primary and secondary inertia masses, the primary and secondary inertia masses being capable of relative rotation against the action of the accumulator,

at least one first friction element rigidly connected to the main mass of inertia for rotation therewith, and at least one second friction element rotating with respect to the first friction element and pressing against the main mass of inertia, the elements being connected to one another by friction, and

a locking member rigidly connected to the secondary inertia mass for rotation therewith, movable under the action of centrifugal force, and rigidly connected to the second friction element when the rotation speed of the engine is lower than a predetermined value,

the locking means form at least one leaf spring configured such that the free end of the leaf spring is positioned, at rest, circumferentially against a stop formed by the second friction element and can be moved away from the stop under the effect of centrifugal force, thereby releasing the second friction element.

Thus, a reliable and repeatable return to the rest position is obtained. In addition, such a device is hardly damaged.

In one embodiment of the invention, the primary inertia mass can be connected to the internal combustion engine and the secondary inertia mass can be connected to the input part of the gearbox.

In one embodiment of the invention, one of the accumulators is an elastic member, such as a coil spring or a leaf spring.

In one embodiment of the invention, the second friction element forms a ring having a radial dimension which varies running along the circumferential direction, said ring extending between a substantially circular inner contour and an outer contour having a variable radial position, a portion of which outer contour forms said stop.

In one embodiment of the invention, the free end has a substantially flat shape capable of following a similar corresponding shape formed by the outer contour of the ring.

In one embodiment of the invention, the stop forms a first surface extending radially from a circle having a first radius to an apex having a second, larger radius, said first surface at its apex being extended by a second surface extending along the circumferential direction, said second surface being extended by a third surface extending along the ramp to said circle having said first radius, the free end of the leaf spring being positioned facing the third surface.

In one embodiment of the invention, the second friction element has a plurality of stops.

In one embodiment of the invention, the locking member comprises a number of leaf springs equal to half the number of stops.

In one embodiment of the invention, the locking member comprises a series of first and second leaf springs arranged in sequence, the free ends of each of the two leaf springs being arranged end to end or in sequence.

In one embodiment of the invention, the locking member forms: an annular first portion rigidly connected to the auxiliary mass for rotation therewith; and a second part comprising a fixed part and a movable part, the free end of the leaf spring being formed by the movable part while extending inside a cylindrical surface formed by the fixed part at rest.

In one embodiment of the invention, the first portion and the second portion extend substantially perpendicular to each other. In particular, the cross-section of the second friction element may be inverted L-shaped.

In one embodiment of the invention, the free end of the leaf spring is able to displace radially outwardly until it is pressed against the secondary mass.

In one embodiment of the invention, the free end of the leaf spring is configured such that it moves away from the stop of the second friction element within a predetermined range of rpm values.

In a preferred example, the free end of the leaf spring is configured such that it moves away from the stop of the second friction element at a rotational speed between 400 and 600 rpm. The stop may be configured such that the free end of the tab no longer contacts the stop above a predetermined number of revolutions per minute. In a preferred example, the free end is no longer in contact with the stop above 600 revolutions per minute.

In one embodiment of the invention, a spring washer is placed between the primary inertia mass and the first friction element in order to cause the second friction element to exert an axial force with respect to the primary inertia mass.

The invention also relates to a method for manufacturing a locking member of a damping device as previously described, characterized in that it comprises the following steps:

the metal plate is cut out, and then,

bending the metal plate around its peripheral edge to obtain a first portion and a second portion comprising the leaf spring, and then

The leaf spring is bent such that its free end is located within the cylinder defined by the remainder of the second portion.

Drawings

The invention will be more clearly understood from reading the following description of non-limiting embodiments of the invention, with reference to the accompanying drawings, in which:

figure 1 shows a partial perspective view of a damping device according to a first embodiment of the invention,

figure 2 shows a partial perspective view of a part of the view in figure 1,

figure 3 shows a partial perspective view of a part of the view in figure 1 from another perspective,

figure 4 shows a perspective view of a locking member according to a first embodiment of the invention,

figure 5 shows a partial perspective view of a second friction washer according to a first embodiment of the present invention,

figure 6 shows a locking member and a second friction washer according to a second embodiment of the invention,

figure 7 shows a partial perspective view of the locking part according to the first embodiment of the invention from a first side,

figure 8 shows a partial perspective view of the locking part according to the first embodiment of the invention from a second side opposite to the first side,

figure 9 shows a view of a metal sheet cut out to obtain a locking member according to a first embodiment of the invention,

FIG. 10 shows a partial cross-sectional view of a secondary flywheel, locking member and second friction washer assembly according to a first embodiment of the invention, an

Fig. 11 shows a graph of the position of the free end of the leaf spring of the damping device according to the first embodiment of the invention as a function of the rotational speed of the engine.

Detailed Description

Fig. 1 to 3 show a damping device 1 according to a first embodiment of the invention. The damping device 1 comprises a primary inertial mass or flywheel 2 and a secondary inertial mass or flywheel 3. An energy accumulator (not shown) is arranged between the primary flywheel 2 and the secondary flywheel 3. For example, a spring or leaf spring may be provided.

The hysteresis device 4 is arranged between the primary flywheel 2 and the secondary flywheel 3. The hysteresis device 4 comprises a first friction washer 5 arranged rotationally fixed relative to the primary flywheel 2 and a second friction washer 6 positioned between the first friction washer 5 and a face 7 of the primary flywheel 2. The support 8 is rotatably mounted with respect to the main flywheel 2. The support 8 comprises means for rotatably connecting the first friction washer 5.

The first friction washer 5 and the second friction washer 6 are placed, by means of a spring washer 9 mounted between the support 8 and the first friction washer 5, pressed against the face 7 of the primary flywheel 2, so that an axial pressure is exerted with respect to the first friction washer 5 and with respect to the second friction washer 5.

A locking member 10 is also provided and is positioned to be rotatably fixedly mounted on the secondary flywheel 3. The locking member 10 forms a first portion 11 fixedly mounted on the secondary flywheel 3 and a second portion 12 comprising a plurality of leaf springs, e.g. 13. In the example of fig. 4, eight leaf springs are formed. Such a locking member 10 may comprise a single leaf spring or more than eight leaf springs.

The first portion 11 has a flat annular shape that is rotatably fixedly mounted on the sub flywheel 3. The second portion 12 forms a stiffness region 21 and a tab 23. The connecting portion 20 connects the first portion 11 to the second portion 12. The stiffness region 21 is configured to provide a degree of motion resilience to the tab 23. To construct this stiffness, additional masses 22 may be added. In the example depicted in fig. 4, the additional mass 22 and the stiffness region 21 are positioned parallel and close to each other. In an embodiment of the invention, the additional mass 22 is formed from a material extending from the tab 23.

In fig. 5, each leaf spring 13 is intended to be positioned, at rest, against a stop 14 formed by the second friction washer 6. The second friction washer 6 forms a ring with variable radial dimensions. The second friction washer 6 is formed with an inner contour 16 of constant size and an outer contour 17 of variable size. In particular, the outer contour has a radially outwardly extending shape in order to form a stop, e.g. 14. In the example of fig. 3 in partial view, seven stops, e.g. 14, can be seen. On such a second friction washer 6 there may be sixteen stops, e.g. 14, as shown in fig. 5.

The stop 14 forms a radially outer projection defining a radial surface 15 against which the free end 24 of the tab 23 of the leaf spring 13 is intended to press. The stop portion 14 further comprises a surface 18 extending the radial surface 15 and extending in the circumferential direction. The surface 18 extends through the inclined surface 19 and then through a surface merging with the surface formed by the rest of the outer contour 17.

"rest" refers to the position of the leaf spring when the engine of the vehicle is not running.

In fig. 7 and 8, the tabs 23 are positioned on two concentric circles at rest. The free end 24 of the tab 23 remote from the rigid region 21 is located on a circle of smaller diameter, compared to the other end of the tab 23 close to said rigid region 21.

Fig. 4 shows that the leaf springs e.g. 13 are positioned one after the other in the circumferential direction. The example in fig. 6 shows another variant of the invention, in which other leaf springs, e.g. 131, are shown, positioned two by two, with their respective tabs, e.g. 131, positioned facing each other. As can be seen in fig. 6, the stop, for example 141, is formed by the outer contour 171 of the second friction washer 51 with two radial surfaces, for example 151, which can accordingly receive pressure from the free ends 241 of the tabs 231 of the leaf springs 131.

In fig. 9, the locking part 10 is made of a metal plate cut into a ring 25, on the periphery of which an arm 26 is cut and formed. These arms form a first portion 27 extending radially and then a second portion 28 and a third portion 29, respectively. The second portion 28 and the third portion 29 extend obliquely with respect to the first portion 27. The second portion 28 is thinner than the first portion 27 and the third portion 29. This second portion 28 will form an area with a stiffness of a predetermined value according to the centrifugal force required to move the free end 24 of the tab 23 away from the stop 14.

The first portion 27 is then bent so that the second portion 28 and the third portion 29 extend in a plane substantially perpendicular to the plane in which the ring 25 extends. The third portion 29 is then bent so that its free end lies in a circle having a diameter smaller than the diameter of the circle in which the second portion 28 extends.

When the engine is started, the main flywheel 2 and the sub flywheel 3 start to move. Under the action of the energy accumulator, the primary flywheel 2 and the secondary flywheel 3 rotate relative to each other. In each rotational movement, the tab 23 is displaced along the circumferential direction so that its free end 24 moves away from the stop 14 and then returns to press against said stop 14. The second friction washer 6 is rotatably connected to the main flywheel 2 each time the free end 24 moves away from the stop 14, without friction. When the free end 24 returns to press against the stop 14, the second friction washer 6 remains rotatably connected to the secondary flywheel 3 and rubs against the primary flywheel 2 during the resulting displacement. These back and forth movements of the free end 24 occur if the engine speed is below 400 revolutions per minute.

Below 400 revolutions per minute, the free end 24 of the tab 23 is placed below the circle that passes over the apex of the stop 14, as shown in fig. 7 and 8. In fig. 11, it can also be seen that below 400 revolutions per minute, a slight radial displacement (between 0.00 and 0.400) occurs.

Between 400 and 600 revolutions per minute, the free end 24 can lift radially outwards away from the second friction washer 6 while moving away from the axis X, so that it no longer presses against the stop 14 during the displacement of the primary and secondary flywheels 2, 3 relative to each other, see fig. 7 and 8. The movement away of the free end 24 is indicated by an arrow in fig. 7 and 8. In fig. 11, it can be observed that the radial displacement lasts between 0.40 and 0.80. From this moment on, the main flywheel 2 and the auxiliary flywheel 3 can rotate relatively without any friction generated by the second friction washer 6. It should therefore be noted that the stop 14 is configured so that above 600 revolutions per minute the end of the tab 13 is no longer in contact with the stop 14.

The tab 23 may even be configured such that it is placed in contact with the primary flywheel 2 after 600 revolutions per minute. Above 1,000 revolutions per minute, as shown in fig. 11, it will be noted that the tab 23 is no longer moving, since it is pressed against the secondary flywheel 3.

Once the rotation speed is reduced, the tab 23 can return to the rest position, i.e. press against the stop 14.