EP1945968A2 - Amortisseur en rangee-parallele a plusieurs etages pour convertisseur de couple - Google Patents

Amortisseur en rangee-parallele a plusieurs etages pour convertisseur de couple

Info

Publication number
EP1945968A2
EP1945968A2 EP06775922A EP06775922A EP1945968A2 EP 1945968 A2 EP1945968 A2 EP 1945968A2 EP 06775922 A EP06775922 A EP 06775922A EP 06775922 A EP06775922 A EP 06775922A EP 1945968 A2 EP1945968 A2 EP 1945968A2
Authority
EP
European Patent Office
Prior art keywords
springs
spring
torque
drive
output
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP06775922A
Other languages
German (de)
English (en)
Inventor
David Avins
Fraser Macdonald
Matthew Frary
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Buehl Verwaltungs GmbH
LuK Lamellen und Kupplungsbau GmbH
Original Assignee
LuK Lamellen und Kupplungsbau Beteiligungs KG
LuK Lamellen und Kupplungsbau GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by LuK Lamellen und Kupplungsbau Beteiligungs KG, LuK Lamellen und Kupplungsbau GmbH filed Critical LuK Lamellen und Kupplungsbau Beteiligungs KG
Publication of EP1945968A2 publication Critical patent/EP1945968A2/fr
Withdrawn legal-status Critical Current

Links

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
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/12353—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
    • F16F15/1236—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
    • F16F15/12366—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
    • F16H2045/0231—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers arranged in series
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0247—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means having a turbine with hydrodynamic damping means
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0294—Single disk type lock-up clutch, i.e. using a single disc engaged between friction members

Definitions

  • the present invention relates to torque converter dampers, and more particularly to such torque converters in which coil springs are inserted in the torque transfer path between the torque converter turbine and an output shaft leading to a transmission to dampen sudden changes in power or torque between the turbine and the output shaft.
  • variable displacement engines operating in four- or eight-cylinder mode has further impeded the reduction of transmission of engine vibration, so that the need for a damper with better control and damping capability (torque absorption capacity for storage) due to the higher torque of the engine Likewise, a lesser degree of coupling, ie, torque capacity per degree of torsional angle, is desirable for noise vibration harshness (NVH), ie, that of a vehicle operator or occupant
  • NVH noise vibration harshness
  • first groups of springs 11 have the form of double spring groups in which an inner spring is disposed within an outer spring, that initially only the outer spring in Action occurs and the inner spring only then parallel to the outer spring in action occurs when the outer spring is compressed far enough.
  • the inner spring must have a smaller diameter than the outer spring and thus is usually much weaker.
  • Such improper weakness can be partially offset by using stronger wire for the inner spring than for the outer spring.
  • the usable spring force of the outer spring is limited by parameters that are unrelated to volume and length. Furthermore, the weaker spring can never be removed from the power transmission.
  • a reliable high-capacity damper which has a large torsion angle, where a low degree of coupling (lower torque per torsion angle) is required at the beginning and the degree of coupling increases more and more with increasing torsion angle.
  • the invention provides a damper for a torque converter.
  • the torque converter itself has a pump that can be driven in the direction of rotation by a motor, and a hydraulic turbine that can be driven in the direction of rotation by the pump.
  • the turbine in turn can be connected via a damper according to the invention with a drive shaft of a transmission.
  • the turbine can rotate around a shaft and is usually provided with a central hub for this purpose.
  • the damper transmits torque from the turbine of the torque converter to an output hub, e.g. is connected to a drive shaft of a transmission.
  • the damper absorb a large part of the excess torque and store it in the form of potential energy, to later release it, if it can be delivered evenly in the form of rotational energy to the transmission.
  • the damper may also act in the reverse direction, ie, store the energy of the excess torque from the transmission when the energy delivered by the engine is less than the energy absorbed due to the inertia of the vehicle and the transmission and absorbs the excess torque and vice versa return to the engine.
  • the damper according to the invention requires a drive unit for receiving the energy of a torque from a drive device such as a motor and an output unit for passing the energy of the torque to an output device such as a transmission.
  • the drive unit is connected to the first ends of the springs of a spring group 1 (first ends of group 1). Second ends of the springs of a spring group 1 (second ends of group 1) abut against first contact surfaces of a sliding device. A second contact surface of the slider abuts against first ends of springs of the spring group 2 (first ends of group 2) and second ends of the spring group 2 (second ends of group 2) abut against the output unit.
  • the slider can move by the acting spring pressure in a first rotational direction freely to a first position between 0 and 99 percent of the spring travel of the spring group 1 and is by a latching unit at a second position between 40 and 90 percent of the spring travel of the spring group 1 with the Drive or driven unit coupled.
  • the sliding device can move by the acting spring pressure in a direction opposite to the first direction of rotation second direction freely to a first position between 0 and 99 percent of the spring travel of the spring group 1 and can by a latching unit at a second position between 40 and 99 percent of the spring travel the spring group 1 are coupled to the drive or the output unit.
  • the output unit is an output plate or hub.
  • the third spring group is arranged between the drive unit and an intermediate flange (or optionally between the drive unit and the output unit) such that first ends of springs of the third spring group are coupled to the drive unit and torque to second ends of the springs of the third group at a position between 5 and 30 percent of the spring travel of the spring group 1 (usually via the intermediate flange) transmitted to the output unit.
  • the spring groups 1 and 2 act in a normal drive direction in series and allow, based on the absorbed torque, a large torsion angle (low “degree of coupling”.)
  • the spring group 3 is parallel to the spring groups 1 and 2 so that the torsion angle related to the absorbed torque is smaller than in the first phase and a greater torque is absorbed per degree of torsion angle (average "coupling degree").
  • the spring group 2 is removed from the series arrangement with the spring group 1, so that each degree of torsion angle more torque is required (high "degree of coupling") .
  • the damper can also act in the opposite direction, ie as a damper for The torque transmitted by the transmission to the engine when the torque absorbed by the transmission in the damper exceeds the torque absorbed by the engine
  • Spring assembly 2 may contain springs of approximately the same strength as the spring assembly 1 or contain stronger or weaker springs Weaker springs than the Spring group 1 may be advantageous so that the start-up coupling degree is lower in the normal operating direction (drive or forward direction).
  • At least one stop between the slider and the drive unit or the output unit removes springs 2 from the series arrangement with the spring assembly 1 and preventsso that the springs of spring group 2 reach their end point. Similarly prevents at least one stop that the springs of the spring group 2 reach their end point in the opposite direction.
  • the damper itself includes a cover plate which is radially aligned with and connected to the turbine, and e.g. It is driven by a turbine hub, concentric with the output hub but free of rotation.
  • An intermediate flange is provided which is also radially aligned with the output hub.
  • An output flange is provided which is connected to the output hub.
  • the springs include a group of drive springs, a group of second springs which may be weaker than the drive springs, and a group of parallel springs which usually have about the same spring characteristics and spring force as the drive springs but optionally another spring force and may have other spring properties.
  • All springs are arranged on a radius around the output hub and housed in the cover plate, so that at a start-up movement of the turbine and the associated cover plate, a first end of the drive springs on the cover plate and a second end of each of the drive springs on the intermediate flange and a first end each of the second springs abuts the intermediate flange and a second end of each of the second springs abuts the output flange so that the drive springs are compressed and transmit a force to the intermediate flange which is rotated to compress the second springs.
  • the second springs turn the output flange and the output hub in rotation.
  • the drive and second springs initially absorb energy from the turbine and allow it to have a greater angle of rotation than the output flange, thereby compensating for the time delay encountered in overcoming the starting inertia of the output hub and the mechanism associated therewith.
  • Parallel springs are housed in openings within the intermediate flange (or in such openings within the cover plate) that are longer than the parallel springs so that the parallel springs do not transmit torque from the cover plate to the intermediate flange due to the rotation upon turbine start-up Cover plate only after sufficient compression of the drive and the second springs far enough over the intermediate flange moves (far enough twisted), so that the parallel springs abut both the cover plate and the intermediate flange and thereby torque from the cover plate to the intermediate flange and then parallel transmitted to the output flange with the drive springs, which further increase the torque capacity transmitted to the output flange with increasing torque.
  • the intermediate flange and the output flange are equipped with stop surfaces, so that the intermediate flange and the output flange abut each other and so the Energy of rotational movement transmitted directly from the intermediate flange to the output flange before the arranged between the intermediate flange and the output flange second springs exceed their end point, so that the drive springs can transmit a parallel torque higher torque via the intermediate flange to the output flange than the second springs.
  • Fig. 1 is a cross-sectional view of a torque converter incorporating a preferred embodiment of a damper according to the present invention.
  • Fig. 2 is an exploded perspective view of the damper part of Fig. 1 in an exploded view.
  • FIG. 3 is a perspective cutaway view of the assembled damper of FIG. 2 as viewed from the driven side of the damper.
  • FIG. 3 is a perspective cutaway view of the assembled damper of FIG. 2 as viewed from the driven side of the damper.
  • Fig. 4 is a view from the driven side of the damper view of the damper of Fig. 3, with cut-out parts at the edge of the cover plate.
  • FIG. 5 shows torque as a function of torsional angle, showing the degree of coupling and the progression of the torque capacity of the damper of FIG. 1.
  • Fig. 6a is a view of the damper of Fig. 3 from the drive side of the damper at a torsional angle of zero degrees at which the drive side of the cover plate is removed.
  • Fig. 6b is a top view of parts of the damper of Fig. 6a at zero torsional angle.
  • Fig. 7a is a view of the damper of Fig. 6a from the drive side of the damper at a torsion angle of 2.4 degrees.
  • Fig. 7b is a plan view of parts of the damper at a torsion angle of 2.4 degrees.
  • Fig. 8a is a view of the damper of Fig. 6a from the drive side of the damper at a torsional angle of 13.82 degrees.
  • Fig. 8b is a plan view of parts of the damper at a torsion angle of 13.82 degrees.
  • Fig. 9a is a view of the damper of Fig. 6a from the drive side of the damper at a torsional angle of 15.5 degrees.
  • Fig. 9B is a plan view of parts of the damper at a torsion angle of 15.5 degrees.
  • Fig. 10 shows a graphical representation of the function of the spring groups within the damper according to the invention, in which the spring group 3 between a drive unit and an output unit in action.
  • Fig. 10a shows a graphical representation of the function of spring groups within the damper according to the invention, in which the spring group 3 between a drive unit and the sliding device in action.
  • Fig. 10b shows a graphical representation of the function of spring groups within the damper according to the invention, in which attacks for the protection of the spring group 2 between a drive unit and an output unit in action.
  • Torsional angle is the relative angle between the damper top plate and the output flange that starts at zero degrees in a “free” position.
  • Free position is the position in which all springs have the lowest compressive force.
  • “Damping capacity” is the ability to absorb torque and is typically measured in Newton meters (Nm), with the absorbed torque retained in the form of potential energy until it is released.
  • the "degree of coupling" of the rotation is equal to the magnitude of the torque absorbed per degree of torsion angle.
  • Hysteresis is the loss of energy that is mostly due to friction during twisting and returning to a free position.
  • “Installation volume” is the volume to be provided for the installation of the damper in the system.
  • Dramper drive means the energy absorbed by the damper either in one direction from the turbine / engine or in one direction from the transmission
  • the description assumes that the drive is always from the turbine to the transmission, but it is clear that the damper can also work in the opposite direction from the gearbox to the turbine.
  • damper output means the energy delivered by the damper either in a direction to the transmission or to the turbine / engine, with the transmission in one direction to a transmission normally being described for simplicity.
  • Percent compression means the linear travel of a coil spring as a percentage of zero or the length of the unloaded spring until reaching the end point of the spring travel where the spring is compressed so far that the individual turns of the spring contact each other.
  • the invention relates to a damper with a large torsion angle for a torque converter with high torque capacity, which is required at the beginning of a lesser degree of coupling, which increases more and more with further rotation.
  • the Construction includes three groups of springs that operate in different torsional phases in series and in parallel.
  • a turbine damper may be included that overrides the turbine mode for six- or eight-cylinder engines. The graded degree of coupling improves power transmission in the three- or four-cylinder mode of engines with disengageable cylinders.
  • the invention relates to a damper for a torque converter.
  • the torque converter itself has a pump that can be rotated by a motor and a turbine that can be hydraulically rotated by the pump.
  • the turbine in turn can be connected via a damper of the invention with a transmission input shaft.
  • the turbine can rotate around a shaft and is usually equipped with a central hub for this purpose.
  • the damper normally causes the transmission of torque from the turbine of the torque converter to an output hub, e.g. to drive a drive shaft of a transmission; however, the damper can also work in the reverse direction.
  • Figures 10, 10a and 10b show a damper of a preferred embodiment of the invention, which is a driven by the force P 1 drive unit 12 (or in the opposite direction by the force P 2 moving output unit 22), eg a turbine, with a Turbine connected plate (cover plate) or connected to the motor plate or shaft needed.
  • the drive unit 12 is connected to first ends 14a of drive springs 14 of a first spring group 1 (first ends of group 1).
  • Second ends 14b of springs 14 of the first spring group 1 (second ends of group 1) abut against the slider 18, eg a freely rotatable disc (intermediate flange), freely movable levers or freely movable cams.
  • the slider 18 abuts first ends 16a of second springs 16 of a spring assembly 2 (first group 2 ends).
  • the slider 18 is free to move to a first position between 0 and 90 percent of the spring travel of springs 14 of the spring assembly 1 under the action of a spring pressure Pi, and the slider 19 latches by latch means 13 at a second position between 40 and 90 percent Spring travel of springs 14 of the spring group 1 with an output unit 22 a.
  • the latching device 13 may, for example, contact surfaces of the output device and the sliding device, one or more latching pins between the output device and the sliding device or Well grooves and wedges exist, or from other devices known in the art.
  • Second ends 16b of springs 16 of the spring assembly 2 abut on the output unit 22, for example a driven pulley or hub.
  • the third spring group 3 can be arranged with springs 17 between the drive unit 12 and the output unit 22, that the first and second ends 17a and 17b of springs of the third spring group on surfaces 13a and 13c of the drive unit 12th or the output unit 22 abut.
  • the embodiment shown in Fig. 10 the third spring group 3 can be arranged with springs 17 between the drive unit 12 and the output unit 22, that the first and second ends 17a and 17b of springs of the third spring group on surfaces 13a and 13c of the drive unit 12th or the output unit 22 abut.
  • the springs 17 of the third spring group 3 may be disposed between the drive unit 12 and the slider 18 such that the first and second ends 17a and 17b of springs 17 of the third spring group are at a position between 5 and 30 Percent of the spring travel of the spring group one on surfaces 13a and 13b of the drive unit 12 and der Gleitvorides 18 abut.
  • Fig. 10b shows a pictorial representation of the function of spring groups within the damper of the invention, in which occur between a drive unit 12 and an output unit 22 for protection stops 13 of the spring assembly 2 in action.
  • the spring groups 1 and 2 act in series under the action of the driving force P1 and allow, with respect to a certain applied torque, a large rotation (low "degree of coupling").
  • a second phase occurs parallel to the spring groups 1 and 2, the spring group 3 is added, so that the rotation, based on a certain applied torque, is smaller and each degree of torsion greater torque is absorbed (average "degree of coupling").
  • a third phase according to FIGS.
  • the spring group is removed from the series arrangement with the spring group 1 (short-circuited) so that an even greater torque is absorbed for each degree of torsion angle (high degree of "coupling") and the springs 16 of the springs are prevented
  • the spring assemblies 1 and 2 are locked together
  • the damper can also operate in the reverse direction, ie as a damper for the torque transmitted from the transmission to the engine, if torque received by the damper from the transmission is greater than the torque absorbed by the damper by the engine
  • One of the spring sets 1 and 2 (normally the spring set 2) may optionally be weaker than the other spring set, so that the degree of coupling is initially lower in the normal operating direction from the engine to the transmission.
  • the torque converter itself a pump 24 which can be rotated by a motor via a cover 20 in turn attached by means of supports 34, directly or ⁇ indirectly to a motor ,
  • a turbine 26 is hydraulically rotated.
  • the turbine 26 in turn may be connected to a drive shaft 32 via a damper 11 according to the invention with a transmission.
  • the turbine can rotate about one turn 32 and for this purpose is usually equipped with a central hub 36 of the turbine.
  • the piston plate 21 connected to the damper 11 is hydraulically moved toward the cover 20, engages the clutch surface 28 with the cover 20, and causes the drive shaft 32 of the transmission to rotate at the same speed as the cover 20.
  • Activation of the hydraulics to displace the piston plate is controlled by a control unit which receives signals from various sensors, such as the relative speeds of the engine and input shaft of the transmission, and changes in torque received and delivered by the torque converter.
  • the damper 11 is normally for transmitting torque from the turbine 26 of the torque converter 10 to an output hub 30 for driving it e.g. to be connected to a drive shaft 32 of a transmission; However, the damper can also be effective in the opposite direction.
  • FIG. 2 to 9b clearly show that the damper 11 itself preferably includes a cover plate 12a / 12b disposed on, connected to and driven by a radius around the turbine 26, eg through the turbine hub 36, concentric is arranged to the output hub 30, but can rotate freely from this.
  • the cover plate 12a / 12b itself consists of cover plate halves 12a and 12b, which are arranged by screws or rivets 12d through connection holes 12c around the other components of the damper 11, wherein the connection holes 12c shown in FIG. 2 on the periphery of the cover plate halves 12a and 12b are arranged.
  • An intermediate flange 18 is provided which is also disposed on a radius about the output hub 30.
  • An output flange 22 is provided which is connected to the output hub 30.
  • the springs include a group 1 of drive springs 14, a group 2 of second springs 16 that are selectively, but not necessarily, weaker than the drive springs 14, and a group 3 of parallel springs 17.
  • All the springs 14, 16 and 17 are disposed on a radius around the output hub 30 and housed in the cover plate 12a / 12b, so that upon a start-up movement of the turbine 26 and the cover plate 12a / 12b attached thereto, a first end 14a of each of the drive springs 14 abuts the cover plate 12a / 12b abuts and abuts a second end 14b of each of the drive springs 14 on the intermediate flange 18 and a first end 16a of each of the second springs 16 on the intermediate flange 18 and a second end 16b of each of the second springs 16 on the output flange 22 (see also Figs FIGS. 10, 10a and 10b).
  • the drive springs 14 are compressed, transmit a force to the intermediate flange 18, rotate it and thus compress the second springs 16 together.
  • the second springs 16 in turn enable the output flange 22 and the driven hub 30 connected thereto to rotate.
  • the drive springs 14 and the second springs 16 absorb energy from the turbine 26 and cause it to rotate through a larger angle ⁇ than the output flange 22, and thus equalize the time delay in overcoming the starting inertia of the output flange 22, the output hub 30 and the mechanism associated with it.
  • the intermediate flange 18 and the output flange 22 are provided with abutment surfaces 13a and 13b, so that the output flange 22 and the intermediate flange 18 abut each other in the forward direction 19 and transmit rotational energy directly from the intermediate flange 18 to the output flange 22, the springs 16 from the series arrangement with the spring assembly 14 are removed and moving the springs 14 in parallel to the springs 17 a larger torque is required, so that a larger torque can be transmitted to the output flange 22 as by parallel to the springs 17 series arrangement of the second springs 16 and the drive springs 14.
  • the parallel springs 17 are housed in openings 17c within the cover plate 12a / 12b and can slide initially within the opening 17d in the intermediate flange, since the opening 17d is longer than the second springs 17, so that the parallel springs 17 at start-up of the turbine 26 of the cover plate 12a / 12b transmitted to the intermediate flange 18 and thus indirectly to the output flange no torque, wherein the cover plate 12a / 12b only after sufficient compression of the drive springs 14 and the second springs 16 far enough against the intermediate flange 18 moves (far enough twisted) so that the parallel springs 17 in the opening 17d slide far enough so that the springs 17 bear against both the top plate 12a / 12b and the intermediate flange 18, so that the parallel springs are parallel to the drive springs 14 (and initially parallel to the second springs 16) )
  • the damper for the torque converter and the method according to the invention have clear advantages, which are illustrated in FIG. 5 in the form of a curve of the torque as a function of the "torsional angle" for a damper according to the invention for a torque converter. It can be seen from the curve that the start-up coupling degree of the damper is very low (soft), so that only a low torque of about 65 Nm or 26 Nm per degree of torsion angle is eliminated on the first 2.5 degree torsion angle. Such a curve causes a significant damping of transmitted through the damper torque shocks when it is too Torque fluctuations between drive and output comes.
  • the first and second spring groups are arranged in series, and the series arrangement and a possibly selected lower strength of the second spring group prevent a high degree of coupling, ie, the first spring group can be compressed relatively far by the action of a certain torque.
  • the torque capacity is greater, ie a torque of up to 400 Nm achieved at a torsion angle of about 12 degrees, but the torsion due to the weaker series arrangement of spring set 1 / spring group 2 and optionally a weaker spring group 2 results in a low degree of coupling of about 32 Nm per degree torsion angle.
  • the spring group 2 is short-circuited, so that only the spring groups 1 and 3 are arranged in series.
  • the degree of coupling can be greatly increased and further prevented that the springs of the spring group 2 reach their end point.
  • the "idle side” of the curve it should be noted that it works in the same way as the "drive side", with only the rotation in the opposite direction taking place.
  • the energy stored by the drive side in the damper is first output to the output side, and then the driven by the transmission output flange 22, the springs 16 in the spring group 2 partially together, which in turn cause the intermediate flange 18, the springs 14 in the To press spring assembly 1 against the cover plate, which is connected via the piston plate 21 either to the turbine or the engine.
  • the springs 17 of the spring group 3 engage, and after sufficiently strong torsion, the spring group 2 is shorted either by the coupling between the intermediate flange 18 and the cover plate 12a / 12b or by the coupling between the intermediate flange 18 and the output flange 22.
  • the spring sets 1 and 2 have the same spring strength or the intermediate flange engages in the forward flange in the output flange to prevent reaching the end point of the spring assembly 2, and the intermediate flange 18 is locked in the opposite direction with the cover plate 12a / 12b to the achievement of the To prevent end point of the spring group 2, there is an idle curve whose slope is equal to the increase of the drive curve.
  • Figures 6A to 9B show the damper according to the invention in different torsional phases, wherein the cover plate, the intermediate flange and the output flange different degrees shifted against each other and the springs are compressed to different degrees.
  • Fig. 6A shows a preferred embodiment of the complete damper according to the invention, in which the parts of the damper are in a neutral position, i. no rotation takes place in the forward or reverse direction.
  • Fig. 6B shows the disassembled parts of the damper of Fig. 6A and their alignment with each other.
  • the drive springs 14 and the second springs 16 respectively occupy 26 degrees of the total angle of the damper of 360 degrees and the parallel springs 19 each 19 degrees of the total angle of the damper.
  • Fig. 7A shows a preferred embodiment of the complete damper according to the invention, wherein the parts of the damper in the forward direction (arrow 19) are twisted by about 2.4 degrees.
  • Fig. 7B shows the disassembled parts of the damper of Fig. 7A and their orientation to each other and how far the springs are compressed.
  • the cover plate is about 2.4 degrees, the intermediate flange by about 1, 2 degrees and the output flange not moved, which shows the alignment of the parts to each other.
  • the movement of the cover plate and the insectsches against each other is determined by the torque fluctuations between the torque absorbed by the engine and the output to the transmission torque and by the ratio of the spring strengths between the spring assembly 1 and the spring assembly 2.
  • Fig. 8A shows a preferred embodiment of the complete damper according to the invention, in which the parts of the damper are rotated by 13.82 degrees in the forward direction.
  • Fig. 8B shows the disassembled parts of the damper of Fig. 8A and their alignment with each other and how far the springs are compressed.
  • the cover plate is about 13.82 degrees, the intermediate flange by about 9 degrees and the output flange not moved, which shows the alignment of the parts to each other.
  • the movement of the cover plate and the insectsches against each other is determined by the torque fluctuations between the torque absorbed by the engine and the output to the transmission torque and by the ratio of the spring strengths between the spring sets 1, 2 and 3.
  • FIG. 9A shows a preferred embodiment of the complete damper according to the invention, in which the parts of the damper are rotated 15.5 degrees in the forward direction.
  • Fig. 9B shows the disassembled parts of the damper of Fig. 9A and their alignment with each other and how far the springs are compressed.
  • the cover plate is about 15.5 degrees, the intermediate flange about 9 degrees and the output flange not moved, which shows the alignment of the parts to each other.
  • the movement of the cover plate and the insectsches against each other is determined by the torque fluctuations between the torque absorbed by the engine and the output to the transmission torque and by the ratio of the spring strengths between the spring sets 1 and 3.
  • the invention also includes a method of damping the torque delivered by the turbine of a torque converter to a transmission as described above with respect to the device.
  • the method includes the following steps:

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

Abstract

L'invention concerne un procédé et un dispositif permettant d'amortir les couples délivrés par la turbine d'un convertisseur de couples à une transmission. Ledit amortisseur comprend les éléments suivants: (a) une unité d'entrée reliée à un moteur; (b) un premier jeu de ressorts comprenant des ressorts d'entrée; (c) un deuxième jeu de ressorts comprenant deux ressorts; (d) un troisième jeu de ressorts comprenant des ressorts parallèles; (e) un dispositif de glissement; et (f) une unité de sortie. Les ressorts du premier groupe de ressorts peuvent être comprimés dans un sens dirigé vers l'avant par rapport à l'unité de sortie, par un couple agissant sur l'unité d'entrée et, dans un sens inverse à l'unité d'entrée, par un couple exercé par l'unité de sortie. Le premier et le deuxième groupe de ressorts sont disposés en série entre l'unité d'entrée et l'unité de sortie, lors d'une première compression vers l'avant, du premier groupe de ressorts et la disposition en série se trouve parallèle au troisième groupe de ressorts entre l'unité d'entrée et l'unité de sortie, lors d'une deuxième compression du premier groupe de ressorts. Le premier groupe de ressorts est disposé en parallèle au troisième groupe de ressorts, sans le deuxième groupe de ressorts, entre l'unité d'entrée et l'unité de sortie, lors d'une troisième compression du troisième groupe de ressorts. Lors de la première compression du premier groupe de ressorts dans le sens avant, le dispositif de glissement se trouve entre l'unité d'entrée et l'unité de sortie et entre les ressorts du premier et du deuxième groupe de ressorts.
EP06775922A 2005-09-08 2006-09-05 Amortisseur en rangee-parallele a plusieurs etages pour convertisseur de couple Withdrawn EP1945968A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US71503405P 2005-09-08 2005-09-08
PCT/DE2006/001553 WO2007028366A2 (fr) 2005-09-08 2006-09-05 Amortisseur en serie/parallele a plusieurs etages pour convertisseur de couple

Publications (1)

Publication Number Publication Date
EP1945968A2 true EP1945968A2 (fr) 2008-07-23

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EP06775922A Withdrawn EP1945968A2 (fr) 2005-09-08 2006-09-05 Amortisseur en rangee-parallele a plusieurs etages pour convertisseur de couple

Country Status (5)

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US (1) US7658679B2 (fr)
EP (1) EP1945968A2 (fr)
JP (1) JP5076117B2 (fr)
DE (1) DE112006002165A5 (fr)
WO (1) WO2007028366A2 (fr)

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Also Published As

Publication number Publication date
DE112006002165A5 (de) 2008-05-21
JP5076117B2 (ja) 2012-11-21
JP2009507194A (ja) 2009-02-19
WO2007028366A2 (fr) 2007-03-15
US20070051577A1 (en) 2007-03-08
US7658679B2 (en) 2010-02-09
WO2007028366A3 (fr) 2007-04-26

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