JP7142532B2 - torsional damper - Google Patents

Description

The present invention relates to torsional dampers.

As shown in FIG. 6, the torsional damper 101 has a structure in which a mass 104 is connected to a hub 102 via a spring 103, and the resonance frequency of the resonance system formed by the combination of the spring 103 and mass 104 is controlled by vibration damping of a crankshaft or the like. By matching the torsional resonance frequency of the object, the function of absorbing the torsional resonance of the vibration isolation object and reducing the vibration is exhibited.

The spring 103 is made of rubber material. Since the rubber material has rigidity in all directions (six degrees of freedom) in addition to the torsional direction (circumferential direction of the torsional damper), it has the function of holding the mass 104 having a predetermined mass at a predetermined position. Therefore, the torsional damper 101 can be established with a simple structure. In addition, since the rubber material has viscoelastic damping characteristics, it already has the damping characteristics required for the torsional damper 101, so that it is easy to exhibit excellent vibration damping performance.

Utility Model Registration No. 2524511 JP-A-5-215202 JP-A-2004-84681

However, rubber materials are generally poor in heat resistance and may not be suitable for mounting inside an engine. In addition, rubber materials generally have poor oil resistance and may not be suitable for mounting inside an engine. Therefore, there is a demand to improve durability such as heat resistance and oil resistance of the torsional damper as a whole including the spring.

An object of the present invention is to improve durability such as heat resistance and oil resistance of a torsional damper.

A torsional damper of the present invention is arranged between a hub provided with first and second spring bearings on the same axis, and between the first and second spring bearings, and is damped to the hub in the circumferential and axial directions via radial bearings. a mass held so as to be displaceable in a direction; a first leaf spring arranged between the first spring bearing and the mass, held by the mass and rotating together with the mass; a first concave portion formed in an end face of the first spring bearing and formed in a valley shape having a tapered surface inclined in one circumferential direction in a direction away from and in a direction approaching the first leaf spring; a first protrusion provided on the first plate spring, forming a mountain-fold shape toward the first spring receiver, inserted into the first recess, and contacting an inner surface of the first recess; and the second spring. a second leaf spring disposed between the bearing and the mass, held by the mass, and rotating together with the mass; a second concave portion formed in a valley shape having tapered surfaces that are inclined in a direction away from the second leaf spring and in a direction toward the second leaf spring; and a second projection that forms a mountain-folded shape facing toward, is inserted into the second recess, and contacts the inner surface of the second recess.

In the present invention, durability such as heat resistance and oil resistance of the torsional damper can be improved.

It is a figure which shows the torsional damper of embodiment, (A) is the perspective view, (B) is the perspective view seen from the back direction. Front view of the same torsional damper (A) is a perspective view of a spring retainer provided in the torsional damper as viewed from the rear, and (B) shows an assembled state of masses, first leaf springs and second leaf springs provided in the torsional damper. Perspective view, (C) is a perspective view of a hub provided in the same torsional damper (A) is a cross-sectional perspective view of the torsional damper cut at the projection position on the circumference, and (B) is a cross-sectional perspective view of the torsional damper cut at the rivet position on the circumference. (A) is a partially cutaway perspective view of the torsional damper, and (B) is a partially cutaway front view of the torsional damper. Half-cut cross-sectional view of the torsional damper described as the background art

As shown in FIGS. 1 to 5, a torsional damper 1 according to the embodiment includes an annular hub 11 attached to a crankshaft (not shown) of a vehicle engine, which is a vibration damping object. 11, a mass (vibration ring) 21, a radial bearing 31 (FIG. 4), a spring holder 41 as a first spring retainer, a first leaf spring 51 and a second leaf spring 61 are assembled.

Each component is formed in an annular shape and arranged coaxially. The hub 11, the mass 21, the spring retainer 41, the first leaf spring 51 and the second leaf spring 61 are each made of metal. The radial bearing 31 is a sliding bearing made of metal such as copper, or made of highly heat-resistant resin such as PTFE. The torsional damper 1 has no rubber parts.

As shown in FIG. 4, the hub 11 has a boss portion 12 fixed to the tip of the crankshaft. An end face portion 13 is integrally provided, a tubular portion 14 is integrally provided from the outer peripheral end portion of the end face portion 13 toward one axial direction, and a second spring bearing is provided radially outward from the outer peripheral end portion of the end face portion 13. A flange portion 15 is integrally provided as a part.

The mass 21 is formed to have a rectangular cross section that is elongated in the radial direction, and is arranged on the outer peripheral side of the cylindrical portion 14 of the hub 11 and on one side of the flange portion 15 in the axial direction.

The radial bearing 31 is formed in a tubular shape and is interposed between the outer peripheral surface of the tubular portion 14 of the hub 11 and the inner peripheral surface of the mass 21 . Since the radial bearing 31 is interposed between the tubular portion 14 of the hub 11 and the mass 21 in this way, the mass 21 is not displaced radially with respect to the hub 11, but is displaced only in the circumferential and axial directions. It is possible.

The spring retainer 41 has a tubular portion 42 fitted and fixed to the outer peripheral surface of the distal end of the tubular portion 14 of the hub 11. A flange portion 43 is integrally provided toward the radially outward direction.

The first leaf spring 51 is formed in a flat annular shape and arranged between the mass 21 and the flange portion 43 of the spring holder 41 . The first leaf spring 51 is fixed to the mass 21 with rivets 71 .

The second leaf spring 61 is formed in a flat annular shape and arranged between the mass 21 and the flange portion 15 of the hub 11 . The second leaf spring 61 is fixed to the mass 21 with rivets 71 .

As shown in FIG. 3A, a first concave portion 44 is provided on the end surface of the flange portion 43 of the spring holder 41 facing the first leaf spring 51 .

The first concave portion 44 has a tapered surface (downward tapered surface) 45 that is inclined in a direction (toward one axial direction) away from the first plate spring 51 toward one side in the circumferential direction (arrow D), Similarly, the tapered surface (upward tapered surface) 46 inclined in the direction of gradually approaching the first leaf spring 51 in one circumferential direction (direction toward the other axial direction) is continuously combined to form a V-shape. , and a plurality of first recesses 44 having such a shape are provided in the circumferential direction (for example, evenly spaced at 8). The inclination angles of the pair of tapered surfaces 45 and 46 (inclination angles with respect to the axis-perpendicular plane) are set equal to each other.

A first projection 52 is provided on the first leaf spring 51 corresponding to the first recess 44 .

As shown in FIG. 3(B), the first projection 52 is directed toward one side of the circumferential direction (arrow D) and gradually approaches the flange portion 43 of the spring retainer 41 (direction toward one side of the axial direction). A tapered portion (upward tapered portion) 53 that is inclined upward, and a tapered portion ( 54 are continuously combined to form a V-shaped mountain fold, and a plurality of first projections 52 having such a shape are provided in the circumferential direction (for example, 8 equipartition). The inclination angles of the pair of tapered portions 53 and 54 (inclination angles with respect to the axis-perpendicular plane) are set equal to each other.

The first protrusions 52 are provided on a portion of the circumference of the first leaf spring 51, and a plane portion 55 is provided between the first protrusions 52 adjacent to each other. Therefore, the first leaf spring 51 is provided with the first protrusions 52 and the flat portions 55 alternately on the circumference, and the first leaf spring 51 is riveted to the mass 21 at the flat portions 55 .

As shown in FIG. 5B, the first protrusion 52 is inserted into the first recess 44 and contacts the inner surface of the first recess 44 . An axial clearance is set between the flat portion 55 of the first leaf spring 51 and the flange portion 43 of the spring retainer 41, and an axial clearance is also set between the rivet 71 and the flange portion 43 of the spring retainer 41. is set. Therefore, the flat portion 55 and the rivet 71 are not in contact with the spring retainer 41 , and only the first projection 52 is in contact with the spring retainer 41 .

When the mass 21 is displaced in one direction in the axial direction and the first plate spring 51 is displaced in one direction in the axial direction accordingly, the first plate spring 51 is pressed against the spring retainer 41 and is elastically deformed to move the shaft. An axial clearance c ₁ is formed between the first plate spring 51 and the mass 21 located on the back side (the other side in the axial direction) of the first protrusion 52 so as to facilitate directional springiness. .

In order to form this axial clearance c1, a concave portion 22 is provided on _one axial end face of the mass 21 . A plurality of concave portions 22 are provided in an equidistant manner (e.g., 8 equidistant locations) in accordance with the first projections 52 .

The circumferential width w ₁ of the recess 22 is larger than the circumferential width w ₂ of the first projection 52 . Therefore, planar axial leaf spring portions (axial deflection portions) 56 which are located on both circumferential sides of the first projection 52 so as to be continuous with the first projection 52 and which do not contact the mass 21 are provided at the ends of the planar portion 55 . is provided. Since the axial leaf spring portion 56 is held in a cantilever manner by the mass 21, it is elastically deformed in _a direction to narrow the axial clearance c1. Therefore, the axial leaf spring portion 56 is a portion of the first leaf spring 51 that exerts an axial spring property.

As shown in FIGS. 2 and 3C, a second concave portion 16 is provided on the end surface of the flange portion 15 of the hub 11 facing the second leaf spring 61 .

The second concave portion 16 has a tapered surface (downward tapered surface) 17 that is inclined in a direction (toward the other axial direction) away from the second plate spring 61 in one circumferential direction (arrow D), Similarly, the tapered surface (upward tapered surface) 18 inclined in the direction of gradually approaching the second leaf spring 61 toward one side in the circumferential direction (direction toward one side in the axial direction) is continuously combined to form a V-shape. , and a plurality of second recesses 16 having such a shape are provided in the circumferential direction (for example, evenly spaced at 8). The inclination angles of the pair of tapered surfaces 17 and 18 (inclination angles with respect to the axis-perpendicular plane) are set equal to each other.

A second protrusion 62 is provided on the second plate spring 61 so as to correspond to the second concave portion 16 .

As shown in FIG. 5, the second projection 62 has a tapered portion (upward tapered portion) inclined in a direction (toward the other axial direction) toward gradually approaching the flange portion 15 of the hub 11 in one circumferential direction. ) 63 is continuously combined with a tapered portion (downward tapered portion) 64 that is similarly inclined in a direction gradually separating from the flange portion 15 of the hub 11 toward one side in the circumferential direction (direction toward one side in the axial direction). A plurality of second protrusions 62 having such a shape are provided in the circumferential direction (for example, evenly spaced at 8). The inclination angles of the pair of tapered portions 63 and 64 (inclination angles with respect to the axis-perpendicular plane) are set equal to each other.

The second projections 62 are provided on a portion of the circumference of the second plate spring 61, and flat portions 65 are provided between the second projections 62 adjacent to each other. Therefore, the second leaf spring 61 is provided with the second protrusions 62 and the flat portions 65 alternately on the circumference, and the second leaf spring 61 is riveted to the mass 21 at the flat portions 65 .

As shown in FIG. 5B, the second protrusion 62 is inserted into the second recess 16 and contacts the inner surface of the second recess 16 . An axial clearance is set between the flat portion 65 of the second plate spring 61 and the flange portion 15 of the hub 11, and an axial clearance is also set here between the rivet 71 and the flange portion 15 of the hub 11. there is Therefore, flat portion 65 and rivet 71 are not in contact with hub 11 , and only second projection 62 is in contact with hub 11 .

When the mass 21 is displaced in the other axial direction and accordingly the second leaf spring 61 is displaced in the other axial direction, the second leaf spring 61 is pressed against the flange portion 15 of the hub 11 and elastically deformed. An axial clearance c2 is formed between the _second plate spring 61 and the mass 21, located on the back side (one side in the axial direction) of the second protrusion 62, so that the spring property in the axial direction can be easily exhibited. ing.

_In order to form this axial clearance c2, a concave portion 23 is provided on the other axial end face of the mass 21 . A plurality of recessed portions 23 are provided in an equidistant manner (e.g., 8 equidistant locations) in accordance with the second projections 62 .

The circumferential width w ₃ of the recess 23 is larger than the circumferential width w ₄ of the second projection 62 . Therefore, planar axial leaf spring portions (axial bending portions) 66 which are located on both sides of the second projection 62 in the circumferential direction so as to be continuous with the second projection 62 and which do not contact the mass 21 are provided at the ends of the planar portion 65 . is provided. Since the axial leaf spring portion 66 is held in a cantilever manner by the mass 21, it is elastically deformed in a direction to narrow the axial clearance _c2 . Therefore, this axial leaf spring portion 66 is a portion of the second leaf spring 61 that exerts an axial spring property.

A mass 21 having a concave portion 22 provided on one end face in the axial direction and a concave portion 23 provided on the other end face in the axial direction is symmetrical in the axial direction. The mass 21 therefore has no axial orientation during its installation.

The first leaf spring 51 in which the first protrusions 52 and the flat portions 55 are alternately provided on the circumference and the second leaf spring 61 in which the second protrusions 62 and the flat portions 65 are provided alternately on the circumference are of the same specifications. considered to be parts. Therefore, both the plate springs 51 and 61 can be used in common.

As shown in the figure, the flange portion 15 of the hub 11 may be provided with through holes 19 for lightening in order to reduce the weight.

5A and 5B show the initial motion posture of the torsional damper 1. FIG. When the torsional vibration on the crankshaft side is input to the torsional damper 1 in this initial motion posture, the mass 21 and the first and second leaf springs 51 and 61 move in the circumferential direction with respect to the hub 11 and the spring holder 41 fixed to the shaft. Displacement (rotation) toward one of them displaces the first and second projections 52 and 62 with respect to the first and second recesses 44 and 16, and the first and second projections 52 and 62 move in the circumferential direction. (the protrusions 52, 62 elastically deform so as to ride on the tapered surfaces 46, 46, 17, 18), an elastic restoring force (reaction force) is generated due to the elastic deformation, and the circumferential direction spring ( torsion spring). Therefore, a torsional resonance system is set by combining with the mass 21 having a predetermined inertia mass, and it is possible to absorb and reduce torsional vibration.

5A and 5B, when axial vibration on the crankshaft side is input to the torsional damper 1 in the initial motion posture shown in FIGS. The second plate springs 51 and 61 are displaced in one direction in the axial direction, and the first and second projections 52 and 62 are displaced with respect to the first and second recesses 44 and 16, respectively. When the mass 21 and the first and second leaf springs 51 and 61 are displaced in one axial direction (leftward in the drawing), the first projection 52 of the first leaf spring 51 presses against the inner surface of the first recess 44. , the _first leaf spring 51 is elastically deformed in the axial direction at the axial leaf spring portion 56 so as to narrow the axial clearance c1. Operate. In the opposite direction, when the mass 21 and the first and second leaf springs 51 and 61 are displaced in the other axial direction (toward the right in the figure), the second projection 62 of the second leaf spring 61 moves toward the second recess 16. When pressed against the inner surface, the _second leaf spring 61 is elastically deformed in the axial direction at the axial leaf spring portion 66 so as to narrow the axial clearance c2. Acts as a directional spring. Therefore, an axial resonance system is set by combining with the mass 21 having a predetermined inertia mass, and it is possible to absorb and reduce the axial vibration. Thereby, the torsional damper 1 also functions as an axial dynamic damper.

The torsional damper 1 configured as described above includes metal first and second leaf springs 51 and 61 instead of conventional rubber springs. 61 is remarkably superior in heat resistance and oil resistance as compared with rubber springs. The torsional damper 1 configured as described above does not include a part made of a rubber material. Therefore, the torsional damper 1 as a whole can be improved in durability such as heat resistance and oil resistance, and the torsional damper 1 can be preferably used in a high-temperature environment or an environment immersed in engine oil.

The torsional damper of the present invention is used, for example, in the field of anti-vibration support for automobile accessories, control devices, electronic devices, and the like. Also, the torsional damper of the present invention is used, for example, in the fields of home appliances and electronic equipment.

REFERENCE SIGNS LIST 1 torsional damper 11 hub 12 boss portion 13 end surface portion 14, 42 cylindrical portion 15 flange portion (second spring bearing)
16 second recess 17, 18, 45, 46 tapered surface 19 through hole 21 mass 22, 23 recess 31 radial bearing 41 spring retainer (first spring receiver)
43 flange portion 44 first concave portion 51 first plate spring 52 first projection 53, 54, 63, 64 tapered portion 55, 65 flat portion 56, 66 axial plate spring portion 61 second plate spring 62 second projection 71 rivet

Claims (3)

a hub provided with first and second spring bearings coaxially;
a mass disposed between the first and second spring bearings and held by the hub so as to be displaceable in the circumferential and axial directions via radial bearings;
a first leaf spring disposed between the first spring bearing and the mass, held by the mass, and rotating together with the mass;
Provided on the end surface of the first spring bearing facing the first leaf spring, the tapered surface is inclined in one circumferential direction in the direction away from and in the direction of approaching the first leaf spring, and has a valley shape. a first recess formed in the
a first projection provided on the first plate spring, forming a mountain-fold shape toward the first spring receiver, inserted into the first recess, and contacting an inner surface of the first recess;
a second leaf spring disposed between the second spring bearing and the mass, held by the mass, and rotating together with the mass;
Provided on the end surface of the second spring receiver facing the second leaf spring, the tapered surface is inclined in one circumferential direction in the direction away from and in the direction of approaching the second leaf spring, and has a valley shape. a second recess formed in the
a second protrusion provided on the second plate spring, forming a mountain-fold shape toward the second spring receiver, inserted into the second recess, and in contact with the inner surface of the second recess;
A torsional damper comprising: A torsional damper according to claim 1,
The first spring receiver comprises a spring retainer fixed to the hub ,
A torsional damper, wherein the second spring bearing comprises a flange integrally provided with the hub . The torsional damper according to claim 1 or 2,
When the mass is displaced in one axial direction and the first projection is pressed against the inner surface of the first recess, the mass is elastically deformed in the axial direction, and the reaction force urges the mass in the other axial direction. A first axial leaf spring portion that exerts an axial spring action is provided as a part of the first leaf spring,
When the mass is displaced in the other axial direction and the second projection is pressed against the inner surface of the second recess, the mass is elastically deformed in the axial direction, and the reaction force urges the mass in the one axial direction. A torsional damper, wherein a second axial leaf spring portion exerting an axial spring action is provided as a part of the second leaf spring.

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