Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
  • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
  • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
  • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
  • F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range

Definitions

• the present invention relates to a pendulum damping device, in particular for a clutch of a motor vehicle transmission system.
• a pendulum damping device is conventionally used to filter the vibrations due to motor acyclisms of a motor vehicle. Indeed, the movements of the cylinders of a combustion engine generate acyclisms which vary in particular according to the number of cylinders. These acyclisms are likely to generate vibrations that can pass into the gearbox and cause shocks and unwanted noise. It is therefore preferable to provide a device for filtering vibrations.
• the pendulum damping device is conventionally fixed rigidly, by means of rivets, to a phasing washer of a torsion damping device, in particular to a clutch, a hydrodynamic torque converter or a double clutch to dry or wet .
• a torsion damping device is for example known as a double damping flywheel.
• the pendulum damping device comprises an annular support intended to be rotated and a plurality of pendular oscillating masses mounted oscillating on the support about an axis parallel to the axis of rotation of the support.
• the displacement of an oscillating mass relative to the support is generally guided by two rolling members each cooperating with a bearing race and a rolling track of the oscillating mass.
• the rolling tracks of the support and oscillating mass extend so that in use the rolling members are in centrifugal and centripetal support, respectively, on said tracks.
• An oscillating mass is conventionally constituted by a pair of weights, sandwiching the support and rigidly secured to each other, generally via a spacer.
• the pendulum damping device rotates at a reduced speed, typically at less than 800 revolutions / min, in particular at start-up, in a slowing phase of the vehicle, during the stopping of the engine or in the case of gearshift, the centrifugal force exerted on the oscillating masses is reduced and the latter therefore tend to approach the axis of rotation.
• the contact of the oscillating masses with the rolling tracks can thus be interrupted, which leads to unwanted noise and shocks that can reduce the life of the pendulum damping device.
• the running gear is a major source of unwanted noise.
• the object of the invention is therefore to provide a more efficient solution for reducing shock and unwanted noise.
• the invention proposes a pendular damping device intended to be integrated in a transmission chain of a motor vehicle, in particular in a clutch, comprising:
• a support having an axis of rotation, and wherein a support window defining a bearing raceway is provided
• an oscillating weight guided in oscillation with respect to the support comprising:
• a spacer matching the flyweights through the support window, a resiliently compressed veneer member in a radial direction relative to the axis of rotation, between the spacer and the support, regardless of the position of the oscillating weight relative to to the support, and in sliding contact on the spacer and / or the support.
• the spacer is pressed radially against at least one rolling member even when the support is rotating at a low speed or zero.
• This plating causes the plating of the at least one rolling member against the support.
• the at least one rolling member is constrained in its radial displacement both by spacer and by the support, and it avoids shocks with the support, or with one or more elements constituting the oscillating mass, sources of noise.
• the inventors have in fact discovered that a plating of the rolling members is more effective than a plating of the weight or weights on the support.
• the veneer member can be in sliding contact only with the spacer, that is to say that it is rigidly secured to the support.
• the plating member may be in sliding contact only with the support, that is to say it is rigidly secured to the spacer.
• the veneer member may be in sliding contact with the spacer and the support, that is to say that it is not rigidly secured to the support or the spacer.
• a device according to the invention may also include one or more of the following optional features:
• the veneer member is attached to the oscillating mass, preferably on the spacer; -
• the oscillating mass comprises a single spacer;
• the veneer member preferably comprises a leaf spring
• the plating member is in sliding contact with a plating track defined by the support and preferably shaped so that the pressure exerted by the plating member on the plating track upon oscillation of the oscillating weight relative to at the carrier, at a constant rotational speed of the support, varies from less than 30%, preferably less than 20%, preferably less than 10%;
• the plating member is in sliding contact with a plating track defined by the spacer and preferably shaped so that the pressure exerted by the plating member on the plating track upon oscillation of the oscillating weight by relative to the support, at constant rotational speed of the support, varies by less than
• said pressure is substantially constant
• More than 50% of the veneer track has more than 70%, more than 90% of its length, one or more depressions arranged so that when the oscillating weight oscillates on one side or the other of a median position, the radial position of the veneer member along a veneer track defined by the support changes during the oscillation;
• the plating track is corrugated by at least 50%, preferably at least 70%, preferably at least 90% of its length;
• the plating track has, in the circumferential direction, a succession of at least two radially offset zones;
• the plating member comprises a part in sliding contact on a spacer and / or the support, preferably with the plating track;
• the part of the plating member is located radially between the spacer and the support, regardless of the position of the oscillating mass relative to the support;
• the entire plating member is located radially between the spacer and the support, regardless of the position of the oscillating mass relative to the support;
• the plating member comprises a pad in sliding contact on the spacer and / or the support, preferably with the plating track;
• the plating member extends in a circumferential direction relative to the axis of rotation (X) between two ends, said ends being in sliding contact on the spacer and / or the support;
• the length of the plating member, in a circumferential direction relative to the axis of rotation (X), is greater than 50%, preferably 80%, of the length, in the circumferential direction, of the spacer ;
• the oscillating mass comprises two spacers between which the plating member is held in contact;
• the oscillating mass comprises a plurality of spacers and the length of the plating member, in the circumferential direction relative to the axis of rotation (X), is greater than 50%, preferably 80%, of the length, according to the circumferential direction, the cumulative length of the spacers;
• the plating member extends between two ends, at least one of said ends forming a loop adapted to be inserted around a pin of the spacer;
• the device further comprises a central abutment, the plating member being movable between a rest position, in which it is remote from the central abutment, and an active position, in which it is in contact with the central abutment.
• the invention also relates to a component for a transmission system of a motor vehicle, the component being in particular a double damping flywheel, a hydrodynamic torque converter or a friction clutch disc, comprising a pendulum damping device according to the invention.
• the invention further relates, in another of its aspects, to a vehicle powertrain comprising:
• FIG. 1 shows a pendulum damping device
• FIGS. 2a and 2b show a first embodiment of the device according to the invention, the support being rotated at low speed or zero;
• FIGS. 3a, 3b, 4a, 4b, 5a, 5b, 6a and 6b illustrate a second, third, fourth and fifth embodiment of the device according to the invention, the support being rotated at low speed or at zero speed .
• the indexed figure "a” represents the device according to the invention in a position centered with respect to its amplitude of oscillation and the indexed figure "b" represents the same device in extreme oscillation position. .
• An “elastic support” generates a pressure from one part to another, unlike a single contact, the elasticity allowing a modification of this pressure by relative movement of these two parts.
• centrifugal support is meant a bearing force comprising a component oriented away from the X axis.
• Crotetal support means a bearing force comprising a component oriented towards the X axis.
• “Motor vehicle” means not only passenger vehicles, but also industrial vehicles, including heavy goods vehicles. , public transport vehicles or agricultural vehicles.
• oscillating weight or "pendulum body” is meant a mass which is mounted to oscillate on the support in response to acyclisms of the vehicle engine.
• An oscillating mass is conventionally constituted by a pair of flyweights, or “pendular masses”, extending so as to sandwich the support and rigidly secured to each other.
• An oscillating mass can also be constituted by a single weight.
• Two pieces are said to be "rigidly secured” or “paired” when they are permanently immobilized relative to each other. This immobilization can result from a fixing of the first part on the second part directly or via one or more intermediate parts.
• the rest position of the device is that in which the oscillating masses are subjected to a centrifugal force, but not to torsional oscillations from the acyclisms of the engine.
• the verb "to include”, “to present” or “to understand” must be interpreted broadly, that is to say, non-limitatively.
• a pendular damping device 10 is shown in FIG. 1. As illustrated, it comprises four oscillating masses mounted on a support 20, each oscillating mass comprising two paired weights 24. One of the weights is not shown to reveal a window 22 support.
• each support window 22 houses a connecting member commonly called "spacer" 12 solidarisant two weights.
• Each oscillating mass may comprise a single spacer.
• each window 22 further comprises two rolling members 18, here rollers.
• An oscillating weight is in fact conventionally mounted oscillating on the support 20 by means of the two rolling members 18 which pass through the support window 22 and guide the movement of the oscillating mass relative to the support 20.
• the rolling members 18 may define a rolling track of support. More particularly, each of the rolling members 18 may comprise a running surface. The running surface is adapted to roll on the support rolling track and the rolling track of the oscillating weight.
• the spacer 12 extends radially between an upper surface and a lower surface.
• the upper surface of the spacer 12 can form the rolling track of the oscillating mass.
• the oscillating masses are preferably distributed equiangularly around the axis X. Preferably, their number is greater than 2 and / or less than 8.
• the device may in particular comprise three, four, five, six or seven oscillating masses. .
• FIGS. 2a and 2b show a close-up view of the pendular damping device 10 shown in FIG. 1, the oscillating mass being respectively in a median oscillation position and in a maximum oscillation position.
• the support 20 is rotated at a low or zero speed, so that the effect of the centrifugal force is not sufficient to press on the one hand the rollers 18 against the support 20 and on the other hand. the other hand the spacer 12 against the rollers 18.
• the speed of rotation of the support is less than a speed of the order of 800 revolutions / minute, preferably lower than a speed of the order 300 rpm.
• the plating of the rolling members is therefore not achieved by the centrifugal force but by the action of a plating member 14.
• the plating track 26 is constituted by all the zones of the support 20 on which the veneer member 14 is, during oscillation of the oscillating mass, in sliding contact.
• the plating member 14 comprises a leaf spring held on the spacer by loops located at both ends of the leaf spring and inserted around pins located on the axial faces. lower and upper the spacer 12. This mounting method advantageously avoids a recess of the plating member 14, for example via its ends, in order to minimize the stiffness of said plating member.
• the plating member 14 may comprise a double leaf spring.
• the sliding contact of the plating member with the plating track 26 of the support is effected by means of a portion 16 of the plating member 14.
• This contact sliding between the plating member 14 and the track of plating 26 may be constant, i.e. there is constantly at least a portion of the areas forming the contact between the plating track 26 and the plating member 14 in contact. This is advantageously in this example of a pad which limits the friction with the support.
• a sliding contact means that at least a portion of the areas forming the contact between the plating track 26 and the plating member 14, more particularly the portion 16, varies as a function of the position of the oscillating mass.
• the sliding contact can be a source of friction.
• the plating member has a length in the circumferential direction greater than 50%, preferably 80%, of the length in the circumferential direction of the spacer. Because of its long length, the veneer member can accept a relatively large deformation while having a low stiffness: thus, the pad can wear out significantly without causing a significant loss of capacity of the organ veneer to perform its plating function. In other words, the durability of the device according to the invention is improved.
• the pad is advantageously made of plastic.
• the pad can be secured to a central portion of the leaf spring.
• the leaf spring is advantageously made of alloy steel for spring or other elastic material.
• the operation of the device according to the invention can be summarized as follows.
• the veneer member 14 experiences the effect of the centrifugal force and is therefore constrained in the radially outer direction.
• the veneer member 14 is then not in contact with the veneer track 26 of the support.
• this improves the performance of the pendulum damping device at high rotational speed.
• the spacer 12 advantageously serves as a radial abutment for the plating member 14, so that the latter is protected from an excessively high radial stress likely to damage it, for example by plasticizing. This case may occur especially in the case of over-revving leading to a speed of rotation, and consequently a centrifugal force, too important.
• the radial stresses undergone by the veneer member are controlled by the invention.
• the veneer member is designed to be in contact with the low-speed rotational support, when the oscillating mass tends to approach the X axis.
• the veneer member With support on the veneer track 26 of the support ( materialized by a thick line in Figures 2 to 4), the veneer member produces a radially outward thrust on the oscillating mass.
• the portion 16 of the plating member 14 slides on the support along the plating track 26 during oscillation of the oscillating mass.
• this plating track 26 is shaped in such a way that the pressure exerted by the plating member on the plating track during oscillation of the oscillating mass with respect to the support, at constant rotational speed of the support, is substantially constant.
• This constant radial pressure of the plating member on the plating track implies that the shape of the plating track 26 is dependent on the shape of the bearing raceway along which the rolling members 18 roll. of the plating track 26 is further dependent on the shape of the plating member 14.
• the plating track 26 has depressions arranged so that when the oscillating mass oscillates on one side or the other other than a median position, the radial position of the veneer member along a veneer track defined by the support changes during the oscillation.
• the veneer track 26 may be corrugated over at least a portion of its length.
• the plating track 26 may have, in the circumferential direction, a succession of at least two radially offset zones in pairs.
• the plating track 26 may have, in the circumferential direction, a succession of at least three radially offset zones in pairs. Thanks to the presence of these depressions, or zones radially offset two by two, the pressure exerted by the veneer member on the veneer track may advantageously remain substantially constant during the oscillation of the oscillating mass.
• Figure 2b shows the oscillating mass in the maximum oscillation position. It is noted that the curvature of the veneer member (and thus also the pressure exerted by the latter on the veneer track) is identical with respect to the median position of the oscillating mass. (in the middle of the two maximum oscillation positions) shown in FIG. 2a, due to the way in which the support plating track is shaped.
• FIGS. 3a and 3b A second embodiment of the invention is illustrated in FIGS. 3a and 3b.
• the second embodiment differs from the first embodiment in that the invention is not limited by the number of spacers 12; this is illustrated by this embodiment.
• the plating member 14, a leaf spring in this example is held in engagement between two spacers 12. A central portion of the leaf spring can form a fastening loop of said leaf spring on the spacers 12.
• This embodiment allows a simplified assembly of the device.
• the part 16 of the plating member in contact with the plating track 26 of the support may be a part 16 of the plating member located at each end of the plating member.
• the veneer track 26 of the support is again shaped so that the pressure exerted by the veneer member on the veneer track remains constant during oscillation of the oscillating weight. Due to the different embodiment of the plating member, the shape of the plating track 26 shown in Figures 3a and 3b differs substantially from the shape of the plating track shown in Figures 2a and 2b.
• the plating track 26 may comprise a circumferential succession of at least five radially offset zones in pairs. Preferably, the plating track 26 may comprise a circumferential succession of at least seven radially offset zones in pairs.
• FIGS 4a and 4b show a third embodiment of a pendulum damping device according to the invention.
• the third embodiment differs from the first embodiment in that the plating member 14 is, in this example, made of a single piece, for example plastic.
• the veneer member may nevertheless be of metal.
• the plating member 14 is elastically deformable and has a spring function.
• Part 16 of the contact member in contact with the plating track 26 of the support is here a part of the veneer member located in the middle thereof. In the middle means that the portion 16 is equidistant from both ends of the plating member 14.
• the 16 may have a substantially hemispherical shape. In this embodiment, it is more particularly the part 16 which, by its shape and position, has a spring function.
• the shape of the plating member 14 is adapted to maintain said plating member 14 on the spacer by clipping thereof on the spacer 12. This mounting method advantageously avoids a recess of the body member. plating 14.
• the third embodiment also differs in that the oscillating mass comprises a central abutment 13.
• the spacer 12 may form the central abutment 13.
• the lower surface of the spacer 12 may comprise a boss forming the central abutment 13.
• the boss may be central, that is to say that it is equidistant from the two ends
• the central abutment 13 may be an outgrowth of the spacer 12.
• the central abutment 13 and the spacer 12 form a single element.
• the central stop 13 and the spacer 12 form two separate elements secured to one another.
• the central stop 13 may have a substantially hemispherical shape.
• the central abutment 13 is adapted to protect the veneer member 14 especially in the case of overspeed leading to a rotational speed, and therefore a centrifugal force, too large (over-strokes in the radial direction).
• the central abutment 13 is further adapted to protect the veneer member 14 in case of saturation of the oscillating weight (over-strokes in the circumferential direction). During these abnormal operations of the oscillating mass, the plating member 14 comes into contact with the central abutment 13.
• the plating member 14 is movable between a rest position and an active position.
• the plating member 14, and more particularly the portion 16 of the plating member 14, is in the rest position, in which it is remote from the central abutment 13, during normal operation of the oscillating mass.
• the plating member 14, and more particularly the portion 16 of the plating member 14, is in the active position, in which it is in contact with the central abutment 13, during abnormal operation of the oscillating mass.
• FIGS. 5a and 5b show a fourth embodiment of a pendulum damping device according to the invention.
• the fourth embodiment differs from the third embodiment in that the clearance between the central stop 13 of the oscillating mass and the plating member 14, when the oscillating weight is in normal operation, is minimal.
• the clearance can be between 0.5 and 2 millimeters or preferably between 0.5 and 1.5 millimeters.
• the veneer member 14 may be of metal.
• the shape of the plating member 14 is adapted to the shape of the spacer 12 and more particularly to the shape of the lower surface of the spacer 12.
• the portion 16 of the plating member 14 may have a shape complementary to the central abutment 13.
• the portion 16 of the plating member 14 may have a hemispherical shape.
• the central abutment 13 is adapted to protect the veneer member 14 especially in the case of overspeed leading to a rotational speed, and therefore a centrifugal force, too large (over-strokes in the radial direction).
• the central abutment 13 is further adapted to protect the veneer member 14 in case of saturation of the oscillating weight (over-strokes in the circumferential direction).
• the plating member 14 comes into contact with the central stop 13.
• the central stop 13 also has a protective role during the assembly of the oscillating mass.
• FIGS 6a and 6b show a fifth embodiment of a pendulum damping device according to the invention.
• the fifth embodiment differs from the fourth embodiment in that each of the oscillating masses comprises two spacers 12.
• the plating member 14 extends circumferentially, preferably integrally, between two ends, each of these ends being in contact, for example by a support, a spacer 12 distinct.
• Each of the two ends may comprise at least one tab adapted to engage axially in holes formed in the flyweights 24.
• the fifth embodiment further differs from the fourth embodiment in that the oscillating mass further comprises a connecting rod 25, forming the central stop 13.
• the connecting rod 25 is adapted to pass through the window 22.
• the connecting rod 25 is distinct from the spacers 12.
• the connecting rod 25 may be movable circumferentially in the window 22 of the support.
• the connecting rod 25 may comprise a main body 25a, for example cylindrical.
• the main body 25a may have an outer surface.
• the outer surface is located radially between the plating member 14 and the support 20. More particularly, the outer surface is located radially between the portion 16 of the plating member 14 and an outgrowth of the support 20 projecting radially into the window 22, circumferentially between the two spacers 12.
• the main body of the connecting rod 25 may be circumferentially offset from the two spacers 12.
• the outer surface is at least one distance from the body The outer surface is adapted to be in contact with the plating member 14 during abnormal operation of the oscillating mass.
• the outer surface of the main body 25a can be adapted to roll on a running surface of the support 20. More particularly, this running surface of the support can be formed by a lower surface of the protrusion of the support 20. The running surface of the main body may further be adapted to roll on the portion 16 of the veneer member 14.
• the connecting rod 25 may further comprise two secondary bodies 25b, for example cylindrical. Each of the secondary bodies 25b is integral with the main body 25a.
• the connecting rod 25 extends axially between one of the two secondary bodies 25b and the other of the two secondary bodies 25b. Each of the two secondary bodies 25b can be integral, in translation and in rotation, with one of the flyweights 24.
• each of the two secondary bodies 25b may have a running surface.
• This running surface is adapted to roll on a race track 24a.
• the feeder bearing track 24a can be formed by a lower surface of one of the flyweights 24. More particularly, the feeder bearing track 24a can be formed by a lower surface of a radial protuberance of the flyweights 24.
• the central abutment 13, formed by the connecting rod 25, is adapted to protect the veneer member 14 especially in the case of overspeed leading to a rotational speed, and therefore a centrifugal force, too important (over-strokes in the radial direction).
• the central abutment 13 is further adapted to protect the veneer member 14 in case of saturation of the oscillating weight (over-strokes in the circumferential direction).
• the veneer member 14 comes into contact with the central abutment
• the plating member 14 is movable between a rest position and an active position.
• the plating member 14, and more particularly the portion 16 of the plating member 14, is in the rest position, in which it is remote from the central abutment 13, during normal operation of the oscillating mass. .
• the plating member 14, and more particularly the portion 16 of the plating member 14, is in the active position, in which it is in contact with the central abutment 13, during abnormal operation of the oscillating mass.
• the central stop 13 also has a protective role during the assembly of the oscillating mass.
• a second plating track 26 can be made on the spacer 12.
• the elastic plating member 14 exerts a radial force, with respect to the X axis, directed outwards on the spacer 12 based on the second plating track 26 of the spacer 12.
• the invention is not limited to the embodiments described and shown, provided for illustrative purposes only.
• the veneer member may be fixed on the support and not on the spacer or more generally on the oscillating weight.
• the different embodiments could also be combined.

Landscapes

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

Priority Applications (3)

Applications Claiming Priority (2)

Publications (1)

Family

ID=61003160

Family Applications (1)

Country Status (5)

Cited By (1)

Families Citing this family (1)

Citations (6)

Family Cites Families (1)

• 2017
  • 2017-10-27 FR FR1760165A patent/FR3073027B1/fr not_active Expired - Fee Related
• 2018
  • 2018-10-26 DE DE112018005016.5T patent/DE112018005016T5/de active Pending
  • 2018-10-26 CN CN201880068307.1A patent/CN111247355B/zh active Active
  • 2018-10-26 WO PCT/EP2018/079427 patent/WO2019081715A1/fr active Application Filing
  • 2018-10-26 KR KR1020207012010A patent/KR20200073231A/ko not_active Application Discontinuation

Patent Citations (6)

Also Published As

Similar Documents

Legal Events