JP5184818B2 - Torsion damping spring - Google Patents

Description

  The present invention relates to a torsionally damped spring and two damped flywheels, and also relates to a double damped pushwheel for an automobile equipped with the torsionally damped spring.

  The double-damping flywheel has two coaxial inertial flywheels that are aligned and guided to each other when rotating, one of which is fixedly mounted at the end of the engine shaft and the other forms the reaction plate of the clutch ing.

  A torsional damping device having a plurality of springs arranged around it is mounted between the two inertial wheels to transmit drive torque from one wheel to the other wheel and to attenuate vibrations from the wheel. The plurality of springs are formed of a metal wire wound in a spiral shape in a free state in a free state, and an end thereof is a stopper fixed to one of the flywheels and an annular fixed to the other one of the flywheels The damper plate is in contact with the radial projection of the damper plate.

  Since the end of the spring is in contact with the protrusion of the stopper and the annular damping plate, many problems occur with respect to the efficiency and life of the spring. One solution is to grind the end turns of each end of the spring to form a flat surface perpendicular to the spring axis on this end turn. This flat surface functions as a surface that abuts the protrusion of the annular damping plate or the final winding of another spring disposed at the first end. However, this grinding process is expensive and weakens the spring winding.

  The object of the present invention is to eliminate the above-mentioned drawbacks in the prior art.

  According to the present invention, a torsional damping spring made of a spirally wound wire that is discontinuous in a free state, and at least at one end of the spring, the second winding from the final winding, or the final winding by a small diameter winding. A torsional damping spring is provided, which is connected to the two previous turns from the winding and extends in a plane substantially perpendicular to the axis of the spring.

  By reducing the diameter of the winding immediately before the final winding, it is possible to obtain the inclination angle of the spiral winding, and therefore the final winding can be formed so as to be substantially orthogonal to the axis of the spring.

  The winding immediately before the final winding, that is, the reduced-diameter winding, is accommodated in the final winding and the winding two before the final winding. The final winding is placed on or in the immediate vicinity of the second winding before the final winding.

  The wire of the coil spring may have a circular cross section, but preferably has a substantially oval or flat cross section.

  In the coil spring according to the present invention, the winding that is curved on the axis of the circle and has a reduced diameter, or the winding immediately before the final winding, is arranged on the radially outer side of the spring so as to be mounted on the torsional damping device.

  Each end of the spring is preferably provided with a final winding connected by a reduced diameter winding to a spring winding two before the final winding, the reduced diameter winding being substantially perpendicular to the axis of the spring. It is.

  The present invention also proposes a double-damping flywheel particularly suitable for automobiles, characterized in that springs of the above-mentioned type are arranged in the circumferential direction.

  The ends of these coil springs are arc-shaped recesses formed on both sides of the alignment protrusions at the radial ends of the protrusions of the annular damping plate that is fixed to one of the plurality of inertia spring wheels of the double-type attenuation spring wheel. Is preferably accepted.

  A double dampening wheel according to a preferred embodiment comprises a plurality of springs of the above-mentioned type formed from a plurality of wires whose ends are abutted and differing in cross section, the winding inclinations of these springs being opposite.

  The wire of the coil spring has a substantially elliptical cross section, the end of which is formed from an arc of a circle with different radii, and the cross section of the wire of the coil spring where the ends are arranged is one coil spring and the other. The cross-section of the wire of one coil spring has a large circular arc inside the winding, and the cross-section of the wire of the other coil spring is the end of a plurality of springs that abut each other. In order to self align, it is preferable to have a small arc inside the winding.

  According to the present invention, while ensuring proper contact of the end of the coil spring against the pawl formed by one of the flywheels and against the radial protrusion of the annular damping plate fixed to the other playwheel. The cost for grinding the end of the coil spring is reduced, and deterioration to the final winding is prevented.

  Furthermore, the final winding of the coil spring contributes to improved transmission of the peak engine torque at which the coil spring is compressed to the maximum and the windings abut each other.

  The service life of a channel inserted between a plurality of coil springs on one of the inertia spring wheels and the radial outer wall of these receiving portions is extended, and this channel is end-fitted by grinding the final winding of the coil spring. It will not be adversely affected.

  DETAILED DESCRIPTION OF THE INVENTION The present invention and its features, details, and effects will be better understood from the detailed description given below with reference to the accompanying drawings.

  A coil spring 10 shown in FIG. 1 is formed by spirally winding a metal wire 12 with a constant diameter. Since the winding of this coil spring is not in close contact in the free state shown in the figure, this coil spring acts as a tension spring and a compression spring, as in the case of a torsion damper in a double-damping flywheel.

  A final winding 14 at each end of the coil spring is connected to a winding 18 two turns before the final winding of the coil spring via a diameter-reduced winding 16 immediately before it.

  Since the diameter of the reduced diameter winding 16 immediately before the final winding 14 of the coil spring is small, this can be inserted into the final winding 14 and the winding 18 two before the final winding. This state is well illustrated, for example, in FIG.

  That is, the diameter-reduced winding 16 is inclined in the direction of the contact surface between the final winding 14 and the two previous windings 18 so as to be contained within the final winding 14 and the two previous windings 18. The outer surface of the final winding 14 forms a flat contact surface that is substantially orthogonal to the axis of the spring.

  Therefore, by grinding the outer surface of the winding of the terminal, the same advantages as those of the conventional coil spring that forms the contact surface orthogonal to the spring and the axis can be obtained. In addition, the disadvantages (high cost of grinding, brittleness of the final winding, wear of the guide channel, etc.) in the conventional one are eliminated.

  In a torsion damper of a double-damping flywheel for an automobile, as shown in FIG. 2, there are two bending angles that are slightly smaller than 90 ° and that have different coil diameters in order to change rigidity. It is advantageous to arrange the ends of the coil springs in abutment.

  In FIG. 2, one of the coil springs whose ends are abutted is indicated by 10, which is formed by a wire 12 having a smaller cross section than the cross section of the wire 22 of the partial coil spring 20. The two coil springs have substantially the same outer diameter.

  The final winding 14 of the first coil spring 10 is connected to a winding 18 two before the final winding via a reduced diameter winding 16 immediately before the final winding, and is substantially orthogonal to the axis of the coil spring 10. Similarly, the final winding 24 of the other coil spring 20 is connected to the two previous windings from the final winding 24 of the coil spring via the reduced diameter winding 26 immediately before the final winding. ing.

  The inclinations of the windings of the two coil springs 10 and 20 are opposite to each other, and the reduced diameter windings 16 and 26 immediately before the final winding are located on the radially outer side of the two coil springs. Therefore, when the coil spring is compressed to the maximum, the reduced diameter winding 16 does not receive a large force.

  Further, as can be understood from the cross-sectional view of the large scale shown in FIG. 5, the wire of the coil spring 10 has a substantially elliptical cross section composed of two arcs of circles c1 and c2 having different radii connected by a straight line segment d. It is advantageous to do so. Here, the radius of the arc of the circle c1 is smaller than the radius of the arc of the circle c2.

  Similarly, the wire of the coil spring 20 has a substantially elliptical cross section consisting of two arcs of circles c′1 and c′2 of different radii connected by a straight line d ′, and the arc of the circle c′1 The radius is smaller than the radius of the arc of the circle c′2.

  As described above, the coil spring 10 and the coil spring 20 have opposite winding inclinations, but the cross-section of the wire of each coil spring is opposite between one spring and the other spring, and the coil spring The arc of the circle c1 with a small radius of the wire 10 is on the radially outer side of the coil spring, and the arc of the circle c2 with a large radius is on the inside of the coil spring.

  For the coil spring 20, the arc of the circle c'1 having a small cross-sectional radius of the wire is located on the radially inner side of the coil spring, and the arc of the circle c'2 having a larger radius is on the radially outer side.

  At the contact interface, that is, the surface where the final winding 14 and the final winding 24 abut, the cross-section of the wire of the coil spring is thus inverted so that the ends of these springs can self-align. ing.

  The final winding 14 of the coil spring 10 can be aligned axially with respect to the final winding 24 of the coil spring 20 because the straight portions of the cross-sections of the wires of these coil springs are constant at the boundary surface. This is because the inclination angle is as follows.

  In FIG. 6 which shows a part of the torsion damper of the double-damping flywheel, there are two sets of the two coil springs 10 and 20 shown in FIG. 2, and the free end thereof is an inertial flywheel of the double-damping pushwheel, for example, the second Abuts against the radial protrusion 30 of the annular damping plate 32 to be fixed to the flywheel.

  Each of the side surfaces 34 of the radial protrusions 30 has two arc-shaped recesses 36 at the radial ends, and the radius of the final winding 14 of the coil spring 10 or the final winding 24 of the coil spring 20, respectively. It is possible to receive the inside in the direction and the outside in the radial direction.

  A portion of the radial side surface 34 between the two recesses 36 forms a centering protrusion for the final winding 14 or 24 of the coil spring, but the dimensions around this centering protrusion are comparable. Therefore, the reduced diameter winding 16 or 26 immediately before the final winding of the coil spring is not damaged.

  Therefore, in order to ensure alignment and contact of the ends of the coil springs 10 and 20 in the torsion damper, machining of the side surface 34 of the radial projection 30 of the annular damping plate can be performed very simply and inexpensively. it can.

It is a typical perspective view of the coil spring by this invention. It is a front view of two coil springs which faced each other by the present invention. FIG. 3 is an enlarged view of a region III indicated by a circle in FIG. 2. FIG. 4 is an enlarged view of a region IV indicated by a circle in FIG. 2. It is an expanded sectional view of the edge part of the coil spring shown in FIG. It is a schematic diagram of a torsion damper for a double-type damping flywheel.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Coil spring 12 Wire 14 Final winding 16 Reduced diameter winding just before final winding 18 Two winding before the final winding 20 Coil spring 22 Wire 24 Final winding 26 Reduced winding just before the final winding 28 Two before the final winding Winding 30 radial projection 32 annular damping plate 34 side surface 36 recess

Claims (8)

A double-compact dampening wheel for an automobile comprising a torsional damping spring made of a metal wire (12, 22) wound in a spiral in a non-continuous arrangement in a free state ,
At least the final winding (14, 24) at one end of the coil spring is connected to the winding immediately before the final winding or two windings before the final winding (18, 28) via the reduced diameter winding (16, 26). And located in a plane substantially perpendicular to the axis of the coil spring ,
The-out reduced-diameter (16, 26) is double the attenuation, characterized in that housed the end winding (14, 24) and the end winding in two before the winding (18, 28) flywheel. 2. The double-damping flywheel according to claim 1 , wherein the final winding (14, 24) is in contact with a winding (18, 28) two before the final winding. 3. A double-damping flywheel according to claim 1 or 2 , characterized in that the cross-section of the wires (12, 22) is circular, substantially elliptical or flat. The double-damping spring wheel according to any one of claims 1 to 3 , characterized in that the torsional damping spring is curved in an arc and the reduced diameter winding (16, 26) is on the radially outer side of the coil spring. . The end windings (14, 24) are connected at their ends to the windings (18, 28) two before the end winding of the coil spring via the reduced diameter windings (16, 26). and wherein the extending substantially perpendicularly to the axis of, double damping flywheel according to any one of claims 1-4. The final windings (14, 24) at the end of the coil spring are formed on both sides of the centering projection on the radial side surface (34) of the radial projection (30) of the annular damping plate fixed to the inertia spring wheel. characterized in that it is received in by arcuate recess (36), double damping flywheel according to claim 1. The double-damping flywheel according to claim 6 , comprising a plurality of coil springs (10, 20) that are end-to-end but formed of wires having different cross-sections. Coil springs (10, 20) have opposite slopes, and have final windings that are substantially perpendicular to the axis of the coil springs and stacked on top of each other. The wire of the coil spring (10, 20) has a substantially elliptical cross section formed by arcs of circles (c1, c′1, c2, c′2) having different radii at the ends, and the ends The cross-sections of the wires of the plurality of coil springs (10, 20) faced to each other are opposite to each other, and one coil spring (for self-alignment of the final windings (14, 24) of the springs in contact with each other) The arc of the circle (c2) having a large cross-sectional radius of the wire of 10) is located inside the winding of the coil spring, and the arc of the circle (c′2) having a large cross-sectional radius of the wire of the other coil spring (20). It is double damping flywheel according to claim 7, characterized in that it is located outside the spring winding.

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