JP5835550B2 - Torsional damper - Google Patents

Description

  The present invention relates to a torsional damper used for absorbing and attenuating torsional vibration generated in a rotating shaft such as a crankshaft in a rotary drive system such as an automobile engine.

  Conventionally, as shown in FIG. 8, a vibration ring (pulley) 53 is connected to the outer peripheral side of the hub 51 via a rubber-like elastic body 52, and a groove portion 54 for winding an endless belt around the outer peripheral surface of the vibration ring 53. There is known a torsional damper provided with (see Patent Document 1).

  Here, an endless belt for driving an auxiliary machine used in an automobile or the like may generate a so-called belt squealing phenomenon in which abnormal noise is generated during operation. This phenomenon is caused by a stick between the endless belt and the pulley groove. There are many slips, and one of the causes is pulley misalignment. As shown in FIG. 9, when the endless belt 55 bites into the pulley 53, there is a misalignment, so that the stickless slip occurs in the process in which the endless belt 55 enters the pulley groove portion 54 obliquely and bites normally. This is because they occur (see Patent Document 2). For this reason, conventionally, it has been necessary to strictly manage the groove position tolerance in order to minimize misalignment.

JP 2010-151217 A JP 2007-198492 A (FIG. 7)

  In view of the above points, the present invention can absorb and reduce misalignment between a pulley and an endless belt without strictly managing the groove position tolerance, thereby suppressing the occurrence of a belt squealing phenomenon. The purpose is to provide a torsional damper.

In order to achieve the above object, a torsional damper according to claim 1 of the present invention connects a vibration ring to the outer peripheral side of a hub via a rubber-like elastic body and winds an endless belt around the outer peripheral surface of the vibration ring. In the torsional damper provided with a groove portion, the vibration ring is formed by a combination of two rings including an inner peripheral mass and an outer peripheral pulley that is axially displaced while rotating around the mass. On the other hand, misalignment between the pulley and the endless belt can be absorbed by the displacement of the pulley in the axial direction.

  A torsional damper according to a second aspect of the present invention is the torsional damper according to the first aspect, wherein the inner peripheral surface of the pulley with respect to a partial recess on the circumference provided on the outer peripheral surface of the mass. The rotation and the axial displacement of the pulley with respect to the mass are set by the engagement of the convex portions provided on the mass.

The torsional damper according to a third aspect of the present invention is the torsional damper according to the second aspect, wherein the concave portion is a resin material holder fitted in a recess provided on the outer peripheral surface of the metal mass. It is formed by the recessed part provided , On the other hand, the said convex part is formed by the convex part provided in the internal peripheral surface of the pulley made of a metal material, It is characterized by the above-mentioned.

  A torsional damper according to claim 4 of the present invention is the torsional damper according to claim 1, wherein a radial bearing is interposed between the mass and the pulley, and the protrusion provided on the outer peripheral surface of the mass and the The protrusions provided on the inner peripheral surface of the pulley engage with the radial bearing, respectively, so that the rotation and axial displacement of the pulley with respect to the mass are set.

  Furthermore, the torsional damper according to claim 5 of the present invention is the torsional damper according to claim 4, further comprising a return spring for returning the axially displaced pulley to the axially initial position. It is characterized by.

  In the torsional damper of the present invention having the above-described configuration, the vibration ring is formed by a combination of two rings including an inner peripheral mass and an outer peripheral pulley, and the pulley is rotated with respect to the mass and axially displaceable. 9 and misalignment between the pulley and the endless belt as shown in FIG. 9 above, the pulley is axially displaced with respect to the mass in the form of being pulled by the tension of the endless belt. Alignment is absorbed.

  As a structure for rotating the pulley with respect to the mass and assembling it so that it can be displaced in the axial direction, the outer circumferential surface of the mass is provided with a concave portion on the circumference and a corresponding convex portion is provided on the inner circumferential surface of the pulley, It is conceivable that the concave and convex portions are engaged with each other. In this case, since the pulley rotates, the engagement between the concave portion and the convex portion is set so as not to play in the circumferential direction. Since the pulley is displaced in the axial direction, the axial direction is intentionally set to play.

  When the concave and convex portions are engaged with each other so as to be axially displaceable as described above, both the mass and the pulley are generally made of a metal material. There are concerns about the occurrence. Therefore, in order to prevent this, it is conceivable to interpose a resin material that is unlikely to generate abnormal noise between metal materials. In this case, specifically, the concave portion is provided on the outer peripheral surface of the metal mass. It forms as a recessed part previously provided in the holder of the resin material engage | inserted by the hollow. On the other hand, the convex portion is preferably formed as a convex portion protruding from the inner peripheral surface of the pulley by pressing a metal pulley, and according to a combination of these, the metallic material is used against the inner surface of the resin concave portion. Since the convex portions of the slidable or slidably contact, the generation of abnormal noise can be suppressed.

  Further, when the vibration ring is divided into the inner mass and the outer pulley as described above and assembled so as to be relatively displaceable, there is a concern that radial play is inevitably generated between the mass and the pulley. Therefore, in order to prevent this, a radial bearing may be interposed between the mass and the pulley. According to this, the radial gap between the mass and the pulley is reduced or eliminated by the bearing. Can be suppressed. In this case, because of the space between the mass and the pulley, the engagement by the combination of the concave portion and the convex portion is difficult to set, so as an alternative, the outer peripheral surface of the mass and the inner peripheral surface of the pulley Protrusions are provided, and the protrusions are engaged with radial bearings. This engagement is the same as described above in that there is no play in the circumferential direction and there is play in the axial direction.

  Further, by providing a return spring that returns the axially displaced pulley to the initial position, the pulley can be automatically returned.

  The present invention has the following effects.

  That is, as described above, according to the torsional damper of the present invention, when there is a misalignment between the pulley and the endless belt, the pulley is pulled by the tension of the endless belt, and the axial displacement is caused with respect to the mass. Thus, misalignment can be absorbed. Therefore, misalignment can be reduced without strictly managing the groove position tolerance as in the prior art, and the occurrence of a belt squealing phenomenon can be suppressed. When a resin holder is interposed between the metal mass and pulley, it is possible to suppress the generation of abnormal noise due to metal touch. When a radial bearing is interposed between the mass and pulley, the mass and pulley The occurrence of radial backlash can be suppressed. When a return spring is provided, the pulley can be automatically returned to the initial position.

The perspective view of the state which cut the torsional damper which concerns on 1st Example of this invention in half 1 is an enlarged view of the main part of FIG. Illustration of the pulley removed from the torsional damper Perspective view of pulley with half cut in the torsional damper Sectional drawing of the principal part of the torsional damper which concerns on 2nd Example of this invention. Perspective view of the torsional damper partly cut away Perspective view of the torsional damper cut out at different cut sections Sectional view of a torsional damper according to a conventional example Illustration of misalignment

  The present invention includes the following embodiments.

(1) In order to achieve the above object, a conventional torsional damper has the following structure.
(1-1) The mass part and the pulley part in the vibration ring are separated (the vibration ring is divided into a mass part and a pulley part), the pulley part is made of sheet metal, and the sheet metal is bent at equal intervals on the inner peripheral side. Set the convex part that consists of. A holder made of a highly lubricious member such as resin is embedded at equal intervals on the outer peripheral side of the opposing mass portion. A hole (concave portion) is set in the central portion of the member made of resin or the like. It becomes the structure in which the convex part of a pulley part enters into this hole.
(1-2) With the configuration of (1-1) above, the pulley portion is movable in the axial direction. Thereby, even if misalignment occurs, the pulley portion moves in the axial direction and the misalignment is cancelled.
(1-3) Moreover, since the pulley part and the mass part are fitted to the holder with a tightening margin with respect to the input in the rotation direction, no rattling sound is generated by the circumferential direction input.
(1-4) According to the configurations of (1-1) to (1-3) above, misalignment is canceled by the pulley portion sliding freely in the axial direction, and TVD belt noise can be prevented. .
(1-5) Further, since the V-groove (groove portion) is movable in the axial direction, the V-groove position tolerance can be set large.

(2) In order to achieve the above object, a conventional torsional damper has the following structure.
(2-1) The mass portion and the pulley portion in the vibration ring are separated (the vibration ring is divided into a mass portion and a pulley portion), and a radial bearing and a pair of axial springs are installed therebetween. Further, the spring constant of the spring is set to be small with respect to the generated load in the axial direction of the belt caused by misalignment. Thereby, even if misalignment occurs, the pulley portion moves in the axial direction, and the misalignment is cancelled.
(2-2) A rotational load is received by the arc-shaped radial bearing and the projections provided on the mass part and the pulley part. It should be noted that the number of protrusions can be arbitrarily set as long as it is equidistant on the circumference.
(2-3) By using a resin-based or non-metallic material as a material for the radial bearing, metal touch with the protrusion due to vibration input is prevented.
(2-4) According to the configurations of (2-1) to (2-3) above, the pulley section slides freely in the axial direction, so that TVD belt noise due to misalignment can be prevented.
(2-5) Protrusions and radial bearings provided on the mass part and the pulley part allow sliding only in the axial direction without impairing the function of transmitting force in the torsional direction.

  Next, embodiments of the present invention will be described with reference to the drawings.

First embodiment ...
1 to 4 show a torsional damper according to a first embodiment of the present invention.

  As shown in FIG. 1 and FIG. 2, a vibration ring 3 is connected to the outer peripheral side of a hub 1 fixed to a rotating shaft (not shown) via a rubber-like elastic body 2. A groove portion 5 having a V-shaped cross section for winding an endless belt (not shown) is provided. As the groove portion 5, a poly V groove including a plurality of V grooves is depicted, but a mono V groove including only one V groove may be used.

  The vibration ring 3 is a metal ring 2 composed of a mass (also referred to as a vibration ring in a narrow sense) 31 disposed on the outer peripheral side of the hub 1 and the rubber-like elastic body 2 and a pulley 41 disposed further on the outer peripheral side thereof. The groove portion 5 is provided on the outer peripheral surface of the pulley 41, and the pulley 41 is rotated (simultaneously rotated) with respect to the mass 31 and is assembled so as to be axially displaceable over a predetermined width. ing.

  The rotation and axial displacement of the pulley 41 with respect to the mass 31 are based on the following structure.

  That is, as shown in FIG. 3, a part of the circumference 31 is provided on the outer peripheral surface of the mass 31, and correspondingly, a part of the circumference is also provided on the inner peripheral surface of the pulley 41 as shown in FIG. The convex portion 42 is provided, and the pulley 41 is rotated with respect to the mass 31 by the engagement of the concave portion 32 and the convex portion 42, and is assembled so as to be axially displaceable over a predetermined width. The engagement is not set in the circumferential direction, but is set in the axial direction. A plurality of the concave portions 32 and the convex portions 42 are provided in an equal distribution (in the figure, 12 equal distributions are assumed).

  The concave portion 32 is formed by a concave portion provided in advance in a resin material holder 34 having a piece shape fitted in a concave portion 33 provided on the outer peripheral surface of the metal mass 31, while the convex portion 42 is formed of a metal. The pulley 41 made of material is formed by a convex portion protruding in a V shape from the inner peripheral surface of the pulley by sheet metal pressing.

  The pulley 41 integrally has the inner peripheral cylindrical portion 43 and the outer peripheral cylindrical portion 44 in contact with each other by folding back the sheet metal into a U-shaped cross section. The convex portion 42 is provided, and the groove portion 5 is provided in the outer peripheral cylindrical portion 44.

  The torsional damper having the above configuration is fixed to the rotating shaft with the hub 1, absorbs and attenuates the torsional vibration generated on the rotating shaft, and winds an endless belt around the groove 5, and rotates from the rotating shaft to various auxiliary machines. Torque is transmitted, and the above-described configuration is characterized in that the following effects are exhibited.

  That is, first, the vibration ring 3 is formed by a combination of two rings including an inner circumference side mass 31 and an outer circumference side pulley 41, and the pulley 41 is rotated around the mass 31 and assembled so as to be axially displaceable. Therefore, if there is a misalignment between the pulley 41 and the endless belt as shown in FIG. 9, the pulley 41 is axially displaced with respect to the mass 31 in the form of being pulled by the tension of the endless belt. Is absorbed. Therefore, misalignment can be reduced without strictly managing the groove position tolerance as in the prior art, and the occurrence of a belt squealing phenomenon can be suppressed.

  In addition, with respect to the engagement between the concave portion 32 and the convex portion 42, the concave portion 32 is formed by a resin material holder 34, and the metallic convex portion 42 is assembled to the concave portion 32 so as to be axially displaceable. Therefore, since the resin and the metal are in sliding contact or contact structure, generation of abnormal noise due to metal touch can be suppressed.

  Further, since the convex portion 42 is formed as a convex portion that protrudes in a V shape from the inner peripheral surface of the pulley by press working, when the pulley 41 is displaced in the axial direction with respect to the mass 31, this V-shaped convex portion is formed. The portion 42 is displaced in the axial direction so that one slope of the V-shape rides on the shoulder of the recess 32, or one of the slopes of the V-shape is pressed against the shoulder of the recess 32 and elastically deforms in the axial direction. At this time, an elastic return force may act in a direction in which the convex portion 42 is returned to the initial movement position. Therefore, when the elastic return force acts in this way, the convex portion 42, that is, the pulley 41 can be automatically returned to the initial movement position. A chamfered slope may be provided on the opening peripheral edge of the concave portion 32 in the holder 34 in order to facilitate the displacement of the convex portion 42 in the axial direction or to facilitate the return movement of the convex portion 42.

Second embodiment ...
5 to 7 show a torsional damper according to the second embodiment of the present invention.

  As shown in FIG. 5, a vibration ring 3 is connected to the outer peripheral side of a hub 1 fixed to a rotating shaft (not shown) via a rubber-like elastic body 2, and an endless belt is connected to the outer peripheral surface of the vibration ring 3. A groove portion 5 having a V-shaped cross section for winding (not shown) is provided. As the groove portion 5, a poly V groove including a plurality of V grooves is depicted, but a mono V groove including only one V groove may be used.

  The vibration ring 3 is a metal ring 2 composed of a mass (also referred to as a vibration ring in a narrow sense) 31 disposed on the outer peripheral side of the hub 1 and the rubber-like elastic body 2 and a pulley 41 disposed further on the outer peripheral side thereof. The groove portion 5 is provided on the outer peripheral surface of the pulley 41, and the pulley 41 is rotated (simultaneously rotated) with respect to the mass 31 and is assembled so as to be axially displaceable over a predetermined width. ing.

  A radial bearing 6 made of a predetermined resin material is interposed between the mass 31 and the pulley 41.

  Further, an outward flange 35 is provided on the outer periphery of one end of the mass 31 in the axial direction, and a stopper 7 is provided on the outer periphery of the other end of the mass 31 in the axial direction (the flange 35 is formed by integral molding. A return spring 8 made of a coil spring is provided between the flange portion 35 and the pulley 41 and between the stopper 7 and the pulley 41 so as to return the pulley 41 displaced in the axial direction to the axial initial movement position. It has been.

  The rotation and axial displacement of the pulley 41 with respect to the mass 31 are based on the following structure.

  That is, as shown in FIG. 7, one circumferential protrusion (outward protrusion) 36 is provided on the outer peripheral surface of the mass 31 and is displaced by 180 degrees so that the inner peripheral surface of the pulley 41 also has one circumferential protrusion. Protrusions (inward protrusions) 45 are provided, and these protrusions 36 and 45 are engaged with the radial bearing 6 so that the pulley 41 is rotated around the mass 31 and can be displaced in the axial direction over a predetermined width. It is assembled to. Therefore, the radial bearing 6 is divided into two parts on the circumference, but instead of dividing into two parts, groove-like recesses extending in the axial direction corresponding to the projections 36 and 45 are provided on the outer peripheral surface of the annular radial bearing 6. May be. In any case, the engagement is not set in the circumferential direction, but is set in the axial direction.

  The pulley 41 has both axial ends of the pulley main body 46 at the center in the axial direction in which the groove portion 5 is provided for the convenience of arranging the radial bearing 6, the flange portion 35, the stopper 7 and the pair of axial springs 8 on the inner periphery thereof. Each of the first and second cylindrical portions 47 having a relatively large inner diameter is integrally formed, and the radial bearing 6 is disposed on the inner peripheral side of the pulley main body 46 at the center in the axial direction. The flange portion 35 and one spring 8 are arranged on the inner peripheral side of the cylindrical portion 47, and the stopper 7 and the other spring 8 are arranged on the inner peripheral side of the other cylindrical portion 47 in the axial direction. Therefore, each spring 8 presses the pulley main body 46.

  The torsional damper having the above configuration is fixed to the rotating shaft with the hub 1, absorbs and attenuates the torsional vibration generated on the rotating shaft, and winds an endless belt around the groove 5, and rotates from the rotating shaft to various auxiliary machines. Torque is transmitted, and the above-described configuration is characterized in that the following effects are exhibited.

  That is, first, the vibration ring 3 is formed by a combination of two rings including an inner circumference side mass 31 and an outer circumference side pulley 41, and the pulley 41 is rotated around the mass 31 and assembled so as to be axially displaceable. Therefore, if there is a misalignment between the pulley 41 and the endless belt as shown in FIG. 9, the pulley 41 is axially displaced with respect to the mass 31 in the form of being pulled by the tension of the endless belt. Is absorbed. Therefore, misalignment can be reduced without strictly managing the groove position tolerance as in the prior art, and the occurrence of a belt squealing phenomenon can be suppressed.

  Further, since the radial bearing 6 is interposed between the mass 31 and the pulley 41, the occurrence of radial play between the mass 31 and the pulley 41 can be suppressed.

  In addition, since the return spring 8 for returning the axially displaced pulley 41 to the initial movement position is provided, the pulley 41 can be automatically returned to the initial movement position. In addition, it is preferable to set pre-compression for the spring 8, and thereby, axial play of each component can be suppressed.

  Moreover, since the radial bearing 6 is interposed between the mass 31 and the pulley 41 and the mass 31 and the pulley 41 are not in direct contact with each other, it is possible to suppress the generation of noise due to the metal touch.

DESCRIPTION OF SYMBOLS 1 Hub 2 Rubber-like elastic body 3 Vibrating ring 5 Groove part 6 Radial bearing 7 Stopper 8 Return spring 31 Mass 32 Concave 33 Depression 34 Holder 35 Flange part 36,45 Protrusion 41 Pulley 42 Protrusion part 43 Inner peripheral cylinder part 44 Outer peripheral cylinder part 46 Pulley body 47 Cylindrical part

Claims (5)

In the torsional damper in which a vibration ring is connected to the outer peripheral side of the hub via a rubber-like elastic body and a groove for winding an endless belt is provided on the outer peripheral surface of the vibration ring.
The vibration ring is formed by a combination of two rings including an outer peripheral side pulley that rotates around the inner peripheral side mass and the mass and is axially displaced ,
A torsional damper characterized in that misalignment between the pulley and the endless belt can be absorbed by the axial displacement of the pulley with respect to the mass. The torsional damper according to claim 1,
The rotation of the pulley relative to the mass and the axial displacement are set by engaging a convex portion provided on the inner peripheral surface of the pulley with a concave portion on the circumference provided on the outer peripheral surface of the mass. Torsional damper characterized by The torsional damper according to claim 2,
The recess is formed by a recess provided in a resin holder fitted in a recess provided on an outer peripheral surface of a metal mass, while the convex is provided on an inner peripheral surface of a metal pulley. A torsional damper characterized by being formed by a convex portion. The torsional damper according to claim 1,
A radial bearing is interposed between the mass and the pulley, and a protrusion provided on the outer peripheral surface of the mass and a protrusion provided on the inner peripheral surface of the pulley engage with the radial bearing, respectively, so that the pulley with respect to the mass is engaged. A torsional damper characterized in that the rotation and axial displacement are set. The torsional damper according to claim 4,
A torsional damper comprising a return spring for returning the pulley displaced in the axial direction to an axially initial position.

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