KR20050016480A - Viscous damper - Google Patents

Abstract

It is a viscous damper which can improve the versatility, make the production easy, and reduce the manufacturing cost. The viscous damper is composed of an annular inertial mass 14 accommodated together with the damping liquid in the case 10 and a hub 11 for fixing the case to the rotation shaft of the internal combustion engine. The case is composed of a case main body 12 having a substantially U-shaped cross section and a cover 7 which tightly closes the opening 12d formed on one side in the axial direction of the main body, and defines a sealed chamber 13 inside. Doing. The inertial mass is formed by overlapping a plurality of annular plates 14a. The inertial mass is axially formed by a thrust bearing 5 attached to the holes 8 of the annular plate on both sides of the inertial mass and a journal bearing 6 mounted on the concave groove 9 of the inner circumference of the inertial mass. It is supported in both sides and the radial direction, and the rotation is arrange | positioned freely in the sealed chamber 13 in the circumferential direction.

Description

Viscose Damper {VISCOUS DAMPER}

The present invention relates to a viscous damper mounted on the shaft of an internal combustion engine such as an automobile engine.

As shown in Fig. 12, the viscous damper for absorbing the torsional vibration of the crankshaft of the internal combustion engine has an opening 2a formed on one side in the axial direction of the annular case body 2 having a substantially U-shaped cross section, with a cover 7. And a ring-shaped inertial mass 4 housed together with the damping liquid (not shown) in the case 3 and the case 3 closed in a liquid-tight manner, and integrally formed in the case body 2. It is bolted to the rotating shaft 1 of the internal combustion engine via the mounting portion 2c.

In the case 3, the sealed chamber 2b is partitioned by the case main body 2 and the cover 7, and the inertial mass 4 is supported by the thrust bearing 5 on both sides of the axial direction, and the inertia The inner circumferential surface of the mass 4 is supported by the journal bearing 6, and the rotation is freely arranged in the sealed chamber 2b in the circumferential direction.

The thrust bearing 5 consists of disks of lubricious materials, such as nylon resin, and is fitted in the shallow mounting hole 8 formed in the both sides of the radial direction of the inertial mass 4 in the radial direction. The thrust bearing 5 abuts the inner surface of the vertical wall opposite to the opening side of the case body 2 and the inner surface of the cover 7 so that the inertial mass 4 is circumferentially with a predetermined narrow gap with these inner surfaces. Rotation supports freely. The journal bearing 6 consists of an annular ring, such as a nylon resin, and is formed by the open ring cut | disconnected in the one part. The journal bearing 6 is disposed between the inner circumferential surface of the inertial mass 4 and the inner surface of the inner circumferential wall of the case body 2, and the inertia mass 4 is rotated in the circumferential direction with a constant narrow gap therein. Support freely (for example, see Japanese Utility Model Registration No. 2579119).

In order to obtain a desired damping characteristic, this viscous damper needs to adjust the inertial mass 4 according to the characteristics of the internal combustion engine to be applied, and if the inertial mass 4 is changed, the case body 2 and the cover 7 are also changed. There is a need. In addition, the inertial mass 4 is generally molded by casting because it is less wasteful of materials and suitable for mass production. However, when the inertial mass is changed, the casting mold must also be changed.

The damping force of the viscous damper originates from the generation of shear resistance in the highly viscous damping liquid present between the case 3 and the inertial mass 4 when a relative speed difference between the case 3 and the inertial mass 4 occurs. Therefore, the damping force is greatly influenced not only by the size of the gap between the case 3 and the inertial mass 4 but also by the surface state of the inner surface of the case 3 and the outer surface of the inertial mass 4. Therefore, the cast inertial mass needs to finish the surface by cutting or the like, which makes the manufacturing process complicated.

In this regard, development of a viscous damper having excellent versatility, easy manufacturing thereof, and reduced manufacturing cost has been desired.

Therefore, the subject of this invention is providing the viscous damper which improves versatility, manufactures it easily, and can also reduce manufacturing cost.

BRIEF DESCRIPTION OF THE DRAWINGS It is sectional drawing which shows the principal part of one Embodiment of this invention hibiscus damper.

FIG. 2 is a plan view showing a part of the annular plate on both sides of the mass of inertia of the viscous damper of FIG. 1. FIG.

It is sectional drawing which shows the principal part of other embodiment of this invention.

4 is a cross-sectional view showing the main parts of still another embodiment of the present invention.

It is a top view which shows the torus plate in which the convex part which can be used for the inertial mass of the viscous damper of this invention was formed.

Fig. 6 is a plan view showing an annular plate formed with a groove that can be used for the inertial mass of the present invention viscous damper.

It is a top view which shows the ring piece used for the torus plate of the inertial mass of the viscous damper of this invention.

FIG. 8: is a top view (a) which shows the improved connection part by tight insertion which connects ring pieces of FIG. 7, and a top view (b) which shows the connection part before improvement.

Fig. 9 is a sectional view (a) showing an annular plate coupled to a dimple and an enlarged cross-sectional view (b) of the dimple.

Fig. 10 is a sectional view (a) and a sectional view (b) after improvement, showing a method of attaching the cover to the case body of the present invention viscous damper before improvement.

It is sectional drawing which shows the coupling of the torus plates by the pin which can be used by this invention.

12 is a cross-sectional view showing a conventional biscus damper.

Disclosure of the Invention

MEANS TO SOLVE THE PROBLEM In order to solve the said subject, this invention provides the case which affixes in the case the fixed case to the rotating shaft of the internal combustion engine which closed the opening toward the axial one side of the ring-shaped case main body which is substantially U-shaped in cross section, and a damping in the said case. A viscous damper comprising a ring-shaped inertial mass accommodated with a liquid and support means for freely rotating the inertial mass in a circumferential direction in the case, wherein the inertial mass is formed by a plurality of annular plates. ) Are superimposed and combined.

In the biscus damper of the present invention, since a plurality of ring plates are laminated to form an inertial mass, the mass of the inertial mass can be easily adjusted according to the increase and decrease of the number of laminated sheets of the ring and the specific gravity of the ring. Therefore, the mass of the inertial mass in accordance with the vibration characteristics of the internal combustion engine to be applied can be easily adjusted, and the versatility of the viscous damper can be further improved.

In addition, mounting of the thrust bearing which is a support means of an inertial mass can also be performed simply by punching a mounting hole in the both annular plates of an inertial mass. The mounting of the journal bearing can also be performed simply by forming a concave groove in the inner circumference of the inertial mass by reducing the inner diameter of the annular plate in the center of the inertial mass.

Although an adhesive agent, a pin, etc. can be used for joining the laminated annular plate, In order to improve productivity, it is preferable to form the engagement piece in the annular plate, and to couple mechanically by a press. According to the present invention, the plurality of ring plates are formed on the surface of the ring plate at intervals in the circumferential direction, and the plurality of ring plates are overlapped and pressurized so that the bent pieces overlap. Can be combined. Or dimples protruding from one side of the annular plate to the other side at intervals in the circumferential direction of the annular plate, and pressing the plural annular plates by overlapping and pressing the dimples in the circumferential direction. The plates can be joined. In this case, it is preferable to form convex portions of the dimples narrower than the concave portions. In this case, the convex portion is well inserted into the surface of the annular plate, and the insertion force increases, thereby increasing the bonding strength between the annular plates. Moreover, the shape stability of the obtained inertial mass becomes favorable.

According to the present invention, preferably, the annular plate is formed by connecting a plurality of ring pieces in an annular shape. Although the torus plate may be punched entirely by a press, it is possible to reduce the waste of materials by assembling a plurality of ring pieces to form the torus plate. According to the present invention, the plurality of ring pieces are disposed in an annular shape, and the plurality of ring pieces are placed in an annular shape by tightly fitting the expansion protrusion pieces formed at one end of the adjacent one ring piece into a hole formed in the corresponding one end of the other ring piece. Can connect In this case, a concave portion may be formed on at least one side of the expansion projection piece base portion of the ring piece, and a convex portion to fit the concave portion on a corresponding side of the opening end of the hole. In this way, even if the hole is pushed out by the expansion projection piece when the expansion projection piece and the hole are tightly inserted, the deformation can be suppressed and absorbed at the fitting portion of the convex portion of the base portion of the hole and the concave portion of the base portion of the expansion projection piece. Therefore, the radially outer portion of the hole of the ring piece can be reliably prevented from spreading outward.

According to the present invention, the inertial mass is formed by stacking annular plates having different inner diameters, thereby forming a comb-toothed concave-convex portion on the inner circumferential surface of the inertial mass, and forming the supporting means on the annular body. On the outer circumferential surface of the indented portion to form a concave-convex fitting with a gap, and the annular body is fixed to the axial position in the case by a spacer or a fixing groove, the inertial mass in the axial direction and the radial direction by the support means Since the rotation can be freely supported in the circumferential direction, the thrust bearing can be omitted, and the processing of the mounting hole can also be omitted. In the case where the annular member is formed of an annular member having a width that abuts against inner surfaces on both sides of the case in the axial direction, machining of spacers and fixing grooves can also be omitted.

Further, the inertial mass is formed by stacking annular plates having different outer diameters, thereby forming a comb-toothed concave-convex portion on the inner circumferential surface of the inertial mass, and forming the supporting means on the annular body, and on the inner circumferential surface of the annular body. An uneven portion of the inertial mass to which the uneven portion of the inertial mass is fitted, having a gap therebetween, except for at least one concave or convex portion of the uneven portion of the annular body; You may have a big gap.

In this way, as in the above, by fixing the annular body in the case with a spacer or a fixing groove in the axial position, the inertial mass can be freely supported in the circumferential direction in the axial direction and the radial direction by the supporting means. Thrust bearings can be omitted, and machining of the mounting holes can also be omitted. Further, by forming the annular body into an annular body having a width that abuts against inner surfaces on both sides in the axial direction of the case, machining of spacers and fixing grooves can also be omitted, which is more preferable. In addition, between the remaining uneven portion of the support means and the unevenness of the inertial mass to which it is fitted, an appropriate gap for generating a desired damping force can be formed by the damping liquid interposed in the gap therebetween, so that the damping force can be added.

According to the present invention, radially convex portions can be formed on outer surfaces of the annular plates on both sides of the axial direction of the inertial mass, and radial grooves are formed on the outer surfaces of the annular plates on both sides of the axial direction of the inertial mass. It can be inclined to the side and formed. In this way, the degree of freedom of damping force adjustment is extended. Further, the case may be fixed to the rotation shaft of the internal combustion engine through a hub having an annular fixing portion for mounting the annular case body. Thus, if a mounting part is not integrally formed in a case main body, formation of a case main body is easy.

Best Mode for Carrying Out the Invention

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of this invention is described in detail based on drawing.

BRIEF DESCRIPTION OF THE DRAWINGS It is sectional drawing which shows the principal part of one Embodiment of this invention hibiscus damper, FIG. 2 is a top view which shows the part of the torus plate used by the inertial mass of the damper of FIG. In the present embodiment, the viscous damper includes a case 10 in which the opening 12d formed on one side in the axial direction of the annular case main body 12 having a substantially U-shaped cross section is sealed with the cover 7 and the case ( 10) a ring-shaped inertial mass 14 accommodated together with the damping liquid, and a hub 11 for fixing the case 10 to a rotation shaft of an internal combustion engine, for example, a crank shaft (not shown) of an automobile engine.

The hub 11 is formed by press-forming a sheet material so as to have an annular fixing portion 11b on its outer circumference, and is attached to the rotating shaft of the internal combustion engine via a mounting hole 11a formed near its center in the radial direction, and the ring of the outer circumference. The case main body 12 is attached to the fixed part 11b of a shape. The case main body 12 is fitted to the annular fixing portion 11b of the hub 11 outer circumference to weld the case main body 12 and the annular fixing portion 11b to the circumferential direction at positions on both sides of the axial direction, The case body 12 is fixed to the annular fixing portion 11b.

The case 10 which closed the opening 12d of the case main body 12 with the cover 17 includes an inner circumferential wall 12a, an outer circumferential wall 12b of the case main body 12 and a vertical wall 12c connecting them; Inside the cover 7, a closed chamber 13 having a substantially rectangular cross section is formed. The inertial mass 14 supports both sides of the axial direction by the thrust bearing 5, supports the inner circumferential surface of the inertial mass 14 by the journal bearing 6, and rotates freely in the sealed chamber 13 in the circumferential direction. It is arranged.

The thrust bearing 5 consists of a disk of lubricable material, such as nylon resin, and is attached to the shallow mounting hole 8 formed in the axial both sides of the inertial mass 14. As shown in FIG. The thrust bearings 5 respectively contact the inner surface of the vertical wall 12c of the case 12 and the inner surface of the cover 7 so as to rotate the inertial mass 14 in the circumferential direction with a predetermined narrow gap with these inner surfaces. I support this freely. The journal bearing 6 is an annular ring made of nylon resin or the like, and is formed of an open ring cut at one part thereof. The journal bearing 6 is attached to the annular shallow concave groove 9 formed in the inner circumferential portion of the inertial mass 14 and fitted on the inner circumferential wall 12a of the case body 12. The journal bearing 6 abuts against the inner surface of the inner circumferential wall 12a of the case main body 12 and freely rotates the inertial mass 14 in the circumferential direction with a predetermined narrow gap therebetween.

The inertial mass 14 consists of a laminated body in which the annular plate 14a is overlapped and bonded, and the mounting holes 8 are formed in the thin annular plate 14a1 located on both sides in the axial direction by punching. The annular plate 14a2 located in the widthwise (axial direction) center portion of the inertial mass 14 has a smaller inner diameter than the other annular plates 14a, 14a1, whereby the inner peripheral portion of the inertial mass 14 The recessed groove 9 is formed.

The case main body 12 can be formed by cold forging of a board | plate material, or press working of a board | plate material. As the plate material, cold rolled steel sheet or steel strip SPCC (for general use), SPCD (for drawing), SPCE (for deep drawing), etc. specified in Japanese Industrial Standard JIS G3141 can be used. By using the board | plate material whose surface is smooth enough practically, such as the said board | plate material, it becomes unnecessary to finish the surface by grinding.

An adhesive may be used to form the inertial mass 14 by joining the annular plate 14a (including the annular plates 14a1 and 14a2), but as described below, a bonding piece is formed on the annular plate 14 to form an annular ring. By pressing the laminate of plates, the annular plates can be mechanically joined to the joining piece. The torus plate 14a itself can be formed by press working of a sheet material. Pressing of the annular plate 14a may be performed by punching the annular plate as a whole, by punching the annular plate into an arc-shaped ring piece which is divided into plural in the circumferential direction. It is good also as a torus. As the plate, SPCC, SPCD, SPCE, etc. may be used. By using the board | plate material whose surface is smooth enough practically, such as the said board | plate material, it becomes unnecessary to finish the surface by grinding.

According to the viscous damper of the present embodiment, since the inertia mass 14 is formed by stacking a plurality of the annular plates 14a, the inertial mass is changed according to the increase or decrease of the number of laminated sheets of the annular plate 14a or the thickness of the toric plate. The mass can be adjusted. In addition, the inertial mass 14 having a high dimensional accuracy can be obtained by pressing the thickness direction with a press. Therefore, the mass of the inertial mass 14 according to the vibration characteristics of the internal combustion engine to be applied can be easily adjusted, and the viscous damper can be made highly versatile. The mass adjustment of the inertial mass 14 can also be easily realized by using an annular plate having a different specific gravity.

Moreover, the mounting hole 8 of the inertial mass 14 to which the thrust bearing 5 is mounted can also be formed by the simple process of punching the both side annular plates 14a1 of the inertial mass 14. The recessed groove 9 on which the journal bearing 6 is mounted can also be easily formed by reducing the inner diameter of the central annular plate 14a2 of the inertial mass 14. In addition, since the case 10 is fixed to the rotation shaft of the internal combustion engine, and the mounting hub 11 is formed separately without integrally forming the mounting portion on the case body 12, the case body 12 can be easily formed.

3 shows another embodiment of the present invention. In this embodiment, the inertial mass 14 was formed by alternately stacking the annular plates 14a3 and 14a4 having different inner diameters, and comb-shaped irregularities (steps) 14A were formed on the inner circumferential surface of the inertial mass 14. Then, the journal bearing 6A is an annular body formed on the outer circumferential surface of the concave-convex 6A1 fitting the concave-convex 14A with a narrow gap, and the inertial mass 14 is supported radially in the bearing 6A. While having an original function, the bearing 6A abuts against the inner surfaces of both sides of the case 10 in the axial direction, that is, the inner surface of the vertical wall 12c of the case body 12 and the inner surface of the cover 7. The width was made to have the function of the thrust bearing which supports the inertial mass 14 in the axial direction.

In this embodiment, one bearing 6A can freely rotate the inertial mass 14 in the circumferential direction in the axial direction and the radial direction, and the processing of the thrust bearing and its mounting hole can be omitted.

4 shows another embodiment of the present invention. In this embodiment, the inertial mass 14 was formed by alternately stacking the annular plates 14a5 and 14a6 having different outer diameters, and the comb-toothed concave-convex portion 14B was formed on the outer circumferential surface of the inertial mass. Moreover, in order to give the journal bearing 6B the original function which supports the inertial mass 14 in radial direction, the unevenness | corrugation 6B1 which fits with the said uneven | corrugated part 14B in the inner peripheral surface of the bearing 6B with a gap is provided. At the same time, the bearing 6B has a width that abuts against the inner surfaces of both sides of the case 10 in the axial direction, and has a function of a thrust bearing for supporting the inertial mass 14 in the axial direction.

At that time, at least one of the unevenness 6B1 of the bearing 6B, in this example, both unevenness 6B1b except for the central convex portion 6B1a, and the unevenness 14B1b of the inertial mass 14 to which it is fitted. The gap between the gaps of the uneven portions 6B1b and 14B1b was made relatively large so that the desired damping force was generated by the damping liquid interposed therebetween. If the damping liquid rotates together with the rotation of the case 10 by the rotation of the shaft equipped with the viscous damper, the damping liquid gathers in the circumferential direction in the sealed chamber 13 by centrifugal force, and the gap between the uneven portions 6B1b and 14B1b. Strong damping force is generated. Therefore, in this embodiment, a strong damping force can be added compared with the viscous damper of FIG. 1 in which unevenness was not formed between the inertial mass 14 and the bearing 6B arrange | positioned at the outer peripheral side.

The central convex portion 6B1a of the bearing 6B and the central concave-convex portion 14B1a of the inertial mass 14 to which the bearing 6B is fitted have a narrow gap to have a radial and axial support function.

In the present invention, as shown in FIG. 5, the radially convex portion 14b can be formed on the outer surface of the annular plate 14a located on both sides of the axial direction of the inertial mass 14. By forming such a convex part 14b, the clearance gap with the inner surface of both sides of the axial direction of the case 10 can be adjusted, and the freedom degree of damping force adjustment is expanded. Moreover, the function of collecting oil can be added to the surface of the inertial mass 14. That is, since the viscus damper generally uses the case 10 in the vertical position from the positioning position of the internal combustion engine, the damping liquid in the closed chamber 13 falls in the stationary state. When the convex portions 14b are formed on both surfaces of the inertial mass 14, the descending damping liquid is easily retained on the surface. Therefore, it becomes possible to exert the damping force in a short time after the internal combustion engine is started.

On both side annular plates 14a of the inertial mass 14, as shown in FIG. 6, the outer surface can be formed by inclining the radial groove 14c to the front end side in the rotational direction. If the groove 14c is formed, the flow of the damping liquid can be changed, so that the damping force can be adjusted. In addition, since the damping liquid inclined in the circumferential direction by centrifugal force when the inertial mass 14 is rotated can be guided to the center direction by the inclined grooves 14c, the journal bearing is the center of the inertial mass 14. It is especially effective when formed in the side. In addition, the convex part 14b and the groove | channel 14c of these torus plate 14a can be formed simultaneously when manufacturing the torus plate 14 by a press.

Although the torus plate 14a of the inertial mass 14 may be punched entirely by a press, it is preferable to assemble a plurality of divided pieces to form a torus plate. As shown in Fig. 7, a plurality of ring segments 21, for example, four or five arc-shaped ring pieces 21 obtained by dividing the annular plate in the circumferential direction are punched from the long plate 20, and one end of the ring piece 21 is simultaneously punched by the punching. The expansion protrusion piece 21b is formed in the hole, and the hole 21a which fits with this expansion protrusion piece 21b is formed in the other end. The ring pieces 21 are arranged in an annular shape by arranging the plurality of ring pieces 21 in the circumferential direction, and bringing the expansion protrusion pieces 21b of the adjacent one ring piece 21 to the holes 21a of the other ring piece 21 and the ring pieces 21. And the end portions of the twenty-seventh parts 21 are pressed, and the end portions touched with each other are pressed to tightly fit the expansion projection pieces 21b into the holes 21a, whereby the plurality of ring pieces 21 are connected to each other to be formed into an annular plate.

In addition, when forming the annular plate 14a by the even ring piece 21, you may form the hole 21a in the both ends of the adjacent one ring piece, and the expansion protrusion piece 21b in the both ends of the other ring piece 21, Similarly, the annular plate 14a can be assembled by tightly inserting the expansion projection piece 21b and the hole 21a.

Thus, when punching from the board | plate material 20 is set as the ring piece 21, the maximum number of sheets of the ring piece 21 which has predetermined | prescribed linear length L from the board | plate material 20 which has the width more than the same width L is made into the maximum number of sheets. By taking it, waste of material can be almost eliminated.

When the expansion projection piece 21b and the hole 21a are tightly inserted, the peripheral portion of the hole 21a of the ring piece 21 is radially expanded because the hole 21a is pushed and widened by the expansion projection piece 21b. In particular, the radially outer portion of the hole 21a is likely to open outward as shown in Fig. 8 (b). Preferably, a rectangular recess 21b1 is formed on both sides of the base portion of the expansion projection piece 21b of the ring piece 21, as shown in Fig. 8A, and the hole 21a of the ring piece 21 is formed. On both sides of the open end, a rectangular convex portion 21a1 is formed to fit with the recess 21b. As shown in Fig. 8 (a), the concave portions 21b1 on both sides of the base portion of the expansion protrusion piece 21b of the ring piece 21 and the convex portions 21a1 on both sides of the opening end of the hole 21a of the ring piece 21 are opened. When fitted, the deformation can be suppressed and absorbed at the fitting portions of the convex portion 21a1 and the recessed portion 21b1, so that the radially outer portion of the hole 21a can be prevented from spreading outward.

In addition, the concave portion 21b1 of the base portion of the expanded projection piece 21b and the convex portion 21a1 of the open end of the hole 21a may be formed only in the outer portion that is easy to open. Moreover, since these recessed parts 21b1 and the convex part 21a1 have strong engagement force, a rectangle is preferable, but it can also be made circular etc. other than a rectangle.

Moreover, in order to ensure the dimension of the torus plate 14, the torus plate 14a may be pressed in the thickness direction, and in this case, the force which spreads to the ring piece 21 is applied, but the recessed part 21b1 of the convex part 21a1 is carried out. If the fitting portion of the ring piece 21 is formed, the shape retainability of the ring piece 21 is good.

Although an adhesive agent can be used for joining the laminated ring 14a, it is preferable to form the engagement piece on the ring 14a, and to mechanically couple | bond by press to improve productivity. The engagement piece is shown in FIG. 7, In this example, half-punching is applied to the center of the circular arc of the ring piece 21, and two half punching pieces 21c (bending pieces) are bent from the surface of the ring piece 21 to protrude. I was.

After the ring pieces 21 are connected to each other to form a torus plate 14a, the plurality of toric plates 14a are overlapped so that the bent pieces 21c overlap. The laminated body of the torus plate is pressed to fit the bent pieces 21c of the overlapping one ring plate to the hole part by the bent pieces 21c formed in the other ring plate, and torus the ring plates together. The annular plates are coupled in an intimate state with substantially no gap by deformation by the press.

Of course, the annular plate forming the bent piece may be a non-connected annular plate punched entirely without connecting the ring pieces, and the non-connected annular plate is formed with a bent piece at intervals in the circumferential direction to similarly form a laminate of the annular plate. Press to combine.

In addition, a dimple may be formed as a joining piece and joined. As shown in FIG. 9, the dimple 22 which protruded from one side surface of the ring piece 21 to the other side was shape | molded by the half piercing process by a press, and the ring piece 21 was connected and formed into the torus plate 14a. Subsequently, the dimples 22 are shifted in the circumferential direction and overlap the plurality of annular plates 14a. Preferably, the dimples 22 overlap each other with the annular plate 14a. And the laminated body of the torus plate 14a is pressed, the convex part 22a of the dimple 22 of the one side torus plate 14a overlapping is inserted in the surface of the other torus plate 14a, and a plurality of torus rings are inserted. Join the plate 14a. The volume of the counter surface plate pushed out by the insertion of the convex part 22a of the dimple 22 moves to the concave part 22b of the dimple 22 to fill the concave part 22b, so that it does not deviate in the outer circumferential direction or the like and has an outer diameter The precision of is good. Moreover, by this, the torus plate 14a is mutually couple | bonded in the substantially closed state.

In this case, it is preferable to form the convex part 22a of the dimple 22 narrower than the recessed part 22b. When the convex part 22a is made narrower than the concave part 22b, the convex part 22a can be formed high by pushing by the half piercing process which obtains the convex part 22a and the concave part 22b simultaneously. Accordingly, the convex portion 22a is well inserted into the surface of the annular plate 14 so that the insertion force is increased to increase the bonding strength between the annular plates 14. Moreover, the shape stability of the obtained inertial mass 14 becomes favorable.

Of course, the toric plate forming the dimple may be a non-connected toric plate punched entirely without connecting ring pieces, and the dimples are formed at intervals in the circumferential direction to the non-connected toric plate, similarly by pressing a laminate of the toric plate to be bonded. do.

According to the present invention, the ring plate 14a can be joined by a pin, a screw, or the like, in addition to the bonding by dimples or the like. Fig. 11 shows the bonding method with a pin. The pinhole 24a is formed in the several places of the circumferential direction of the torus plate 14a. The annular plate 14a may be punched out as a whole by pressing as in the past, or may be bonded by punching with an arc-shaped ring piece, and press molding the hole 24 during the punching or after the punching. Pins having a plurality of annular plates 14a overlapping the pin holes 24 so as to overlap each other, and having a recessed recess 25a at both ends in the pin holes 24 of the laminate of the annular plates 14a ( 25) are inserted, the caulking jig (not shown) of substantially the same shape is applied to the recesses 25a at both ends thereof, and the recesses 25a are expanded to the state indicated by the solid line in the state indicated by the double-dotted line. The pin 25 is caulked to join the laminated ring 14a.

In this case, in order to prevent the end part of the pin 25 from protruding outward from the laminated body of the torus plate 14a, the pinhole 24 of the torus plate 14a located in the outermost layer as shown in the figure is opened. It is preferable to enlarge the diameter toward the outside by chamfering or the like so that the edge 24a can absorb the deformation | transformation excess of the edge part of the pin 25. If the pin 25 is made rather short, it is not necessary to have a deformation margin.

The viscous damper may be integrally formed in the case main body 12 and mounted directly on the rotating shaft of the internal combustion engine, but as described above, the hub having the annular fixing part 11b on the outer circumference of the case main body 12 ( 11) was mounted on the rotating shaft through the hub (11). As shown in FIG. 10, the case main body 12 is fitted to the outer peripheral portion of the annular fixing portion 11b of the hub 11, and then the inner peripheral wall 12a and the annular fixing portion of the case main body 12. The circumferential welding 15a, 15b is performed to 11b at both axial direction positions, and it joins. If strength is acceptable, spot welding may be used.

The cover 7 which closes the opening 12d of the case main body 12 is also joined to the opening end by welding, as shown in FIG. 10 (a) or (b). Fig. 10A shows the same mounting method as in the prior art. The inner end wall 12a and the outer circumferential wall 12b of the case main body 12 are subjected to end processing to form inner and outer end portions 12e obtained by cutting the inner side of the open end portion. The upper and lower ends of the cover 7 are inserted into the 12e, and the entire circumferential welding is performed in the circumferential direction between the upper and lower ends of the cover 17, the outer peripheral wall 12b of the case body 12, and the abutment portions of the inner peripheral wall 12a. 15c (only the upper side is shown in the figure), the cover 7 is hermetically joined to the opening end of the case main body 12.

10 (b) is an improved mounting method. The tip of the annular fixing portion 11b of the hub 11 protrudes from the opening end of the case body 12, and the cover 7 is placed on the tip of the protruding annular fixing portion 11b. To the opening end of the case main body 12, and welds 15d and 15e to the abutment portions of the upper and lower ends of the cover 17 and the outer circumferential wall 12b and the inner circumferential wall 12a of the case main body 12 in the circumferential direction. The cover 7 to the opening end of the case main body 12 in a liquid-tight manner, and weld 15e the lower end of the cover 17 and the inner circumferential wall 12a of the case main body 12. ), The open end side of the case main body 12 and the annular fixing portion 11b of the hub 11 are joined at the same time. It is preferable to use beam welding, laser welding, or the like for the welding.

According to this mounting method, the lower end of the cover 17 and the inner circumferential wall 12a of the case main body 12, the open end side of the inner circumferential wall 12a of the case main body 12, and the annular shape of the hub 11 are provided. Since the welding of the fixed part 11b of this invention can be completed without performing welding separately, welding work can be reduced.

As described above, according to the biscus damper of the present invention, since the annular inertial mass contained together with the damping liquid is formed by overlapping and combining a plurality of ring plates, the number of laminated sheets of the ring plate is increased or decreased. The mass of the inertial mass can be easily adjusted, and the versatility of the damper pulley can be further improved.

Claims (12)

A case fixed to the rotational shaft of the internal combustion engine, which is tightly closed by a cover with an opening facing toward one axial side of the annular case body having a substantially U-shaped cross section, and an annular inertial mass housed together with the damping liquid in the case. And a support means for freely rotating the inertial mass in the circumferential direction in the case, The inertial mass is a biscus damper, characterized in that formed by combining a plurality of ring plate overlap. The bent pieces are formed on the surface of the toroidal plate at intervals in the circumferential direction, and the plurality of toric plates are joined by overlapping and pressing the bent pieces so that the bent pieces overlap. Viscose Damper. The method according to claim 1, wherein dimples protruding from one side of the annular plate to the other side are formed at intervals in the circumferential direction of the annular plate, and the plurality of annular plates are alternately pressed by shifting the dimples in the circumferential direction. Viscus damper, characterized in that the plurality of ring plate combined. The viscous damper according to claim 3, wherein the convex portion of the dimple is formed narrower than the concave portion. The said torus plate is a biscus damper according to any one of claims 1 to 4, wherein a plurality of arc-shaped ring pieces are connected in an annular shape. 6. The plurality of ring pieces according to claim 5, wherein the plurality of ring pieces are arranged in an annular shape, and the plurality of ring pieces are ring-shaped by tightly fitting the expansion protrusion pieces formed at one end of the adjacent one ring piece into a hole formed at the corresponding one end of the other ring piece. Vickers damper, characterized in that connected in the shape. 7. The viscous damper according to claim 6, wherein a concave portion is formed on at least one side of the expansion projection piece base portion of the ring piece, and a convex portion is fitted on the corresponding side of the opening end of the hole. 8. The comb-shaped concave-convex portion is formed on the inner circumferential surface of the inertial mass, and the support means is formed in a ring-shaped body according to any one of claims 1 to 7. And a concave-convex portion formed on the outer circumferential surface of the annular body with a gap formed therebetween. 8. The comb-shaped concave-convex portion is formed on the outer circumferential surface of the inertial mass, and the support means is formed in a ring-shaped body according to any one of claims 1 to 7. At the same time, the concave and convex portions are formed on the inner circumferential surface of the annular body to fit the concave and convex portions of the inertial mass, and the remaining concave and convex portions other than the at least one concave or convex portion of the concave and convex portion thereof are provided. A biscus damper characterized by having a large gap with the uneven portion of the inertial mass to which the remaining uneven portion is fitted. 10. The viscous damper according to any one of claims 1 to 9, wherein radially convex portions are formed on outer surfaces of the annular plates on both sides of the axial direction of the inertial mass. 10. The viscous damper according to any one of claims 1 to 9, wherein a radial groove is formed on the outer surface of the annular plate on both sides of the axial direction of the inertial mass so as to be inclined at the front end side of the rotational direction. 12. The viscous damper according to any one of claims 1 to 11, wherein the case is fixed to the rotating shaft of the internal combustion engine through a hub having an annular fixing portion for mounting the annular case body.