SE443618B - TWO-STEP TORSION SWITCH ABSORPERS - Google Patents

Description

8008026-0 2 10 15 20 25 30 35 Under certain operating conditions of the vehicle's engine and transmission, a damping speed lower than the lowest speed obtainable in the above-mentioned dampers is desired and this lower speed can be achieved with the present two-stage damping arrangement.

The invention also relates to a torsional vibration damper which, due to its very low damping speed, increases the hydraulic damping which is built into a hydraulic torque converter for the vehicle. Without a locking coupling, the torque converter hydraulically dampens unwanted vibrations, resonance, etc., but a separate damper is required when arranging the locking coupling. Existing dampers with extended movement provide a sufficiently low damping speed to allow the hydraulic damping in the torque converter to work and increase the effect of the vibration damper.

The invention further relates to a new two-stage torsional vibration damper which has two concentric circles of damping springs arranged in a housing and which is driven by drive flaps mounted on a driving element such as a piston plate for the locking coupling. Floating elements separate the springs in both the inner and outer spring circles and two or more groups of springs in each circle work in parallel with the springs in each group working in series.

The invention also relates to the provision of a new two-stage torsional vibration damper which has concentric circles of springs, the springs in the outer circle being driven by drive tabs and separated within the spring groups by floating dividing rings which have dividing arms between adjacent springs. In the inner circle of springs driven by bracket elements on the holder housing, floating wedges or sliding means which are movable in the holder housing adjoin adjacent springs. The inner spring groups finally drive the arms of a hub element which is operatively connected to the input shaft of the vehicle transmission.

The invention further relates to the provision of a two-stage torsional vibration damper having concentric circles of springs arranged in two or more groups where the springs 10 in each group are separated by floating wedges or sliding means.

Another feature of the invention is the provision of a two-stage torsional vibration damper which provides a low damping speed with a maximum arc for relative movement between the driving and driven elements of 900. The device has an outer circle of springs arranged in three groups operating in parallel with three spring sets in each group and an inner circle of springs arranged in two parallel groups with three spring sets in each group.

Additional purposes are to achieve a design with maximum simplicity, efficiency, economy and simple assembly and operation and such additional purposes, advantages and possibilities which are set forth in more detail below.

A method of realizing the invention is described in detail in the following with reference to the drawings which show only a particular embodiment. Fig. 1 shows a rear view with parts removed in the two-stage vibration damper. Fig. 2 shows on a larger scale a cross section of the damping device taken along the irregular line 2-2 in Fig. 1 arranged in a torque converter. Fig. 3 shows on a larger scale a partial section taken along line 3-3 in Fig. 1. Fig. 4 shows on a larger scale a partial section taken along line 4-4 in Fig. 1. Fig. 5 shows a rear view of the front holder plate in the device. Fig. 6 shows a cross-section of the front holding plate taken along the irregular line 6-6 in Fig. 5. Fig. 7 shows a partial section taken along the line 7-7 in Fig. 5. Fig. 8 shows a rear view of the rear holding plate. Fig. 9 shows a cross section through the rear holding plate taken along the irregular line 9-9 in Fig. 8. Fig. 10 shows a partial section taken along the line 10-1 in Fig. 8. Fig. 11 shows a side view partly in section of the inner sliding sub-angle element in operative position. Fig. 12 shows on a larger scale an exploded view in perspective of an inner, sliding dividing element. Fig. 13 shows a rear view with certain parts broken away by a second embodiment of two-stage vibration dampers. Fig. 14 shows a partial section through the device taken along the irregular line 14-14 in Fig. 13. Fig. 15 shows a side view, partly in section, of an outer, sliding dividing element in operative position. Fig. 16 shows a side view of the outer partition element. Fig. 17 shows an end view of the outer dividing element.

Fig. 18 shows a horizontal section through the dividing element taken along the line 18-18 in Fig. 16. Fig. 19 shows a section taken after the irregular line 19-19 in Fig. 16.

Fig. 20 is a perspective view of a seat plate for the dividing element. Fig. 21 shows a rear view with some parts broken away by a third embodiment of a two-stage vibration damper. Fig. 22 shows a cross section through the damping device taken after line 22-22 in Fig. 21. Fig. 23 shows a section taken after line 23-23 in Fig. 21. Fig. 24 shows a section taken after line 24-24 in Fig. 21.

As can be seen in more detail from the drawings which show illustrative embodiments of the invention, Figs. 1 and 2 show a two-stage torsional vibration damper device 10 used in a 1-coupling 11 for a torque converter 12. The torque converter comprises a housing 13 driven by the output shaft of a motor (not shown) having a front cover 14 with an annular coupling surface 15 formed on its inner surface and a rear cover 16 operatively connected to an opening wheel1 (not shown). A turbine 17 is arranged in the front part of the housing and is attached at its inner periphery 18 to a turbine hub 19 which has internal boom grooves 21 which receive the boomed end of an input shaft 22 in the transmission. A stator (not shown) is also suitably arranged in the housing.

An axially movable piston plate 23 has an annular friction surface 24 within the outer periphery which cooperates with the surface 15 and forms the coupling 11 and an inner annular flange 25 slidably mounted on a bearing 26 and sealed by an annular ring seal 27 mounted in a groove 1 mounted in a groove.

Both the coil plate 23 and the damping device 10 are arranged in the space between the front housing 14 and the height of the turbine 17.

The vibration damper 10 comprises three peripherally spaced drive tabs 28 attached to their base members 29 to the piston plate 23 by means of two or more rivets 31 with the tabs extending radially inwardly in a housing formed by a front retainer plate 32 and a rear retainer plate 32. In order for the flaps to be able to move relative to the housing, the substantially parallel peripheral flanges 37,52 on the plates 32,33 are fastened together at a plurality of points around the periphery by means of locking pins 34, each pin having a central extended part 35 which acts as a spacer. between the flanges with the ends 36 of the pins passing through the openings 38.53 in the flanges and sprained. Thus, the flanges are separated by the parts 35 to allow the flaps to extend into and move relative to the housing. The front holding plate 32 is circular with an irregular cross-sectional shape as shown in Figs. 5, 6 and 7 and has an annular peripheral flange 37 provided with openings 38 for the rivets or locking pins 34, an intermediate part 39 connected to the peripheral flange by means of three outer drive members. element 41 and an inner peripheral portion 42 which is substantially conical and is connected to the intermediate portion 39 by means of a pair of oppositely arranged connecting arms 43, 43, each connecting arm having an inwardly offset central inner drive bracket 44.

The outer drive elements 41 in conjunction with the peripheral flange 37 and the intermediate portion 39 define three elongate arcuate grooves or openings 45 for the groups of outer damping springs 73, 74 and 75, each opening being further defined by an outer arcuate lip 46 on the flange 37 and an inner arcuate lip 47 on the intermediate portion 39. Likewise, the connecting arms 43 in combination with the intermediate portion 39 and the inner portion 42 form a pair of elongate, arcuate grooves or openings 48 for the groups of inner damping springs 76, 77 and 78, the intermediate portion 39 having a spring retainer lip 49 extending in the opposite direction to the lip 47. The inner periphery 42 converges inwardly toward a central opening 51.

The rear retaining plate 33 includes a peripheral flange 52 having circumferentially spaced openings 53 which receive the locking pins 34 and a central portion 54 connected to the peripheral flange by three circumferentially equally spaced drive elements 5580 205 * 25 30 35 55 The drive members define three arcuate grooves or openings 56 which are substantially axially aligned with the grooves 45 and have outer lips 57 on the flange 52 and inner lips 58 on the portion 54. The central portion 54 is curved rearwardly to form closed pockets 59 for the damping springs 76, 77 and 78 and has a pair of inwardly offset oppositely arranged inner drive tabs 61. The body terminates in an inwardly extending radial flange 62 which defines a central opening 63 substantially axially in line with the opening 51 in the front plate 32.

On a rearwardly extending annular flange 64 of the front retaining plate 32 are mounted a pair of dividing rings 65 and 68, of which the ring 65 has three equally spaced circumferentially spaced slightly offwardly offset dividing arms 66 which extend radially outwardly and terminate in circumferentially extending fingers 67. Likewise. the ring 68 has three equally spaced circumferentially spaced dividing arms 69 which extend radially outwards and terminate in circumferentially extending fingers 71. The arms 66 and 69 are oppositely offset so that they and their respective fingers 67 and 71 extend into a guide channel 72 formed between the peripheral flanges 37 and 52 and the outer lips 46 and 57 on the front and rear plates, respectively.

Arranged between the outer drive elements 41 and 55 on the plates 32 and 33 and the arms 66 and 69 on the rings 65 and 68 are three groups of damping springs 73, 74 and 75 which operate parallel to the springs in each group acting in series. Similarly, two groups of damping springs 76, 77 and 78 operating in parallel are arranged in the inner spring pockets 59 between the drive tabs 44 and 61 and pairs of sliding dividing elements 79 and 81. Each dividing element comprises a conical body 82 which ends at the wide end in an arcuate sliding part 83 which extends circumferentially from the two diverging edges 84, 84 of the body. A dividing member clamp 85 has a pair of outwardly diverging sides 86, 86 connected by a rounded connecting member 87 which fits on the conical body 82 in each dividing member, which arms terminate in outwardly extending flanges 88 which contact the inner members. the surfaces of the arcuate sliding part 83. The sides 86, 86 extend outwards at 89 beyond the width of the conical body so that they are contacted by the damping springs 76, 77, 78. The sliding parts 83 in the dividing elements cooperate with a guide surface 91 formed on the central part 54 of the plate 33 and the extended sides 89 fit in the spring pockets 59 between the plates.

A hub assembly 92 includes a hub sleeve 93 with inner boom grooves 94 which cooperate with outer boom grooves 95 formed on the turbine hub 19 and a hub plate or flange 96 disposed on the sleeve and extending between the plates 32 and 33 at their inner periphery. The flange 96 comprises a pair of diametrically opposed hub arms 97.97 extending between and substantially axially aligned with the pair of drive tabs or stirrups 44 and 61, which arms have outwardly diverging edges 98 and terminate in circumferentially opposite extending fingers 99. Thus, the hub arms 97 lie in the path of the inner damping springs 76, 77 and 78. Likewise, the radial flange 62 on the rear plate 33 is mounted on the hub sleeve 93.

The outer arcuate lips 46 and 57 on the plates 32 and 33 have re-entry surfaces 101 and 10 2 formed adjacent to the drive elements 41 and 55 and act both as holders for the springs 73 and 75 and as inclined planes to prevent outward movement of the springs when the drive brackets 28 moved away from the elements 41.55 during the attenuation.

During operation of the torque converter 12, the oil flowing in the vanes of the impeller, turbine and stator will also fill the torque converter housing 13 and as the oil pressure increases with increasing rotational speed of the turbine 17 the oil pressure gradually pushes the piston plate 23 and associated damping device 10 to the left in Figure 2. and brings the friction surface of the piston plate into contact with the surface l5 of the front cover lä to lock the impeller and the turbine in the torque converter in a direct drive arrangement. Assuming that the piston plate is rotated in the counterclockwise direction seen in Fig. 1, the piston plate 23 and the drive brackets 28 begin to rotate when the coupling surfaces come into contact relative to the stationary damper housing.

As the drive brackets move between the flanges 37, 52 on the retaining plates 32, 33, they contact the damping springs 73 and compress the springs. The springs 73 force the rear dividing ring 68 via the arms 69 to compress the springs 74, which springs in turn force the arms 66 of the front dividing ring 65 to compress the springs 75.

These springs in turn act on the outer drive elements 41, 55 on the plates 32,33 and rotate the plates relative to the hub assembly 92. Rotation of the plates 32 and 33 causes the inner drive brackets 44,61 to compress the pair of springs 76 and these springs contact and moves the sliding divider members 79 so that the springs 77 are compressed, the springs 77 moving the sliding divider members 81 to compress the springs 78. Compressing the springs 78 forces the arms 97 of the hub assembly 92 to rotate the hub sleeve 93 and the turbine sleeve 93. results in rotation of the input shaft 22 of the transmission.

Thus, the device dampens any vibration, noise, etc. in the drive transmission with an arrangement in which three groups of outer springs 73, 74, 75 are used in parallel and two groups of inner springs 76, 77, 78 in parallel, the springs in each group acting in series .

Figures 13 to 20 show a second embodiment of two-stage vibration dampers similar to that shown in Figures 1 to 12, similar parts having the same reference numerals with the appendix a. In this embodiment a second series of sliding dividers 103 and 104 is used instead of the front ones. and rear divider rings 65 and 68, shown in Figs. These dividing elements slide on the outer lips 46a and 57a on the front pouring plate 32a and 32a, respectively. the rear holding plate 33a. The dividing means 103 and 104 are identical and are formed of punched sheet metal with outwardly diverging sides 105 having inwardly curved edges 106 and connected by a rounded inner end 107, the sides terminating at their outer ends in circumferentially extending flanges having flanges 108 l09 as 10 15 20 25 30 35 8008026-0 is accommodated in openings 111 in a substantially rectangular s1it plate 110 which extends on the fins 108. S1it plate1 contacts the outwardly extending 1appers_46a and 57a on the holder plates with the figs 109 accommodated in the guide channel 72a between the fins 37a and 52a for controlling the movement of the dividing elements.

During operation upon rotation of the piston plate 23a, the drive tabs 28a relatively move the holder plates 32a and 33a and contact the springs 73a. Compression of these springs forces the springs against the sliding swingarms 103 to compress the springs 74a, which in turn forces the sliding swings 104 against the springs 75a. Compression of the springs 75a causes the drive members 41a, 55a to rotate the holder plates 32a, 33a which causes rotation of the drive members 44a, 61a toward the inner springs 76a. Compression of the springs 76a forces the splitting means 79a to compress the springs 77a which in turn forces the splitting means 81a to compress the springs 78a which springs contact the hub arms 97a to rotate the hub assembly 92a which causes rotation of the transmission.

Figures 21-24 show a third embodiment of a two-stage damper device 112 similar to that of Figures 1-12, wherein similar parts have the same reference numeral with the addition of the letter b. The housing plate 23b is substantially the same as shown in Figure 2 except for a According to the 113 on which a pair of oppositely arranged drive tabs 114 are fastened with screws 115 or similar fastening means. Each drive flap has a conical body with outwardly diverging spring contacting surfaces 116 projecting into an arcuate base portion 117, the blade having a sloping surface 118 abutting the coil plate, an oppositely substantially vertical surface 119 and an upwardly extending guide flange 120. a peripheral groove 121 extends through the conical body and into the base.

Mounted on the drive members is a dividing ring 122 (Figs. 22, 23 and 24) having a sloping surface 123 abutting the coil plate 23b, a flat underside 124 with an annular groove 125 receiving the guide flanges 120 and a pendant. The inner flange 126 is parallel to the substantially vertical surface 117 of the tabs. At opposite ends, the ring has a pair of inwardly extending thicker portions 127 and each portion terminates in a conical dividing member 128 having inwardly converging spring contacting surfaces 129. A pair of sliding dividers 130 (Figs. 21 and 24) are mounted to slide in the chute which is each partition member comprises a conical body 131 having outwardly converging spring contacting surfaces 132 and an arcuate base 133 having an outwardly projecting surface 134 cooperating with the outwardly facing surface 113 of the piston plate, an arcuate surface 135 1 degree in the underside 124 of the ring. 122 and a flat surface 136 which slidably cooperates with the inner surface of the hanging flange 126.

A member 137 includes an outer ring 138 having a pair of oppositely directed arms 139 (Fig. 22) with outwardly diverging spring contacting edges extending in circumferentially extending fingers 141 and an inner ring 142 connected to the outer ring by a pair of opposed means. drive tabs 143 having outwardly diverging spring contacting edges 144, the tabs being connected to the inner ring by means of offset members 145.

An inner drive ring or hub 146 (Fig. 22) includes a ring having a pair of oppositely inwardly extending drive vanes 147 with inwardly converging spring contacting surfaces and a rearwardly facing inwardly extending annular hub flange 148 which is suitably attached, e.g. , to the torque converter1's turbine hub 19b. The ring 146 and the tabs 147 have elongate peripherally extending grooves 151 which receive the drive tabs 143 for relative rotation between the melange 137 and the drive ring 146. On the ring 146 are rotatably mounted two pairs of divider elements 152, 153 which have inwardly converging surface contacting springs the inner damping springs 76b, 77b and 78b. The dividing elements 128 on the ring 122 and the sliding dividing elements 130 separate the outer damping springs 73b, 74b and 75b.

As can be seen from Fig. 16, there are two groups of damping springs 73b, 74b, 75b acting in parallel and two groups 10 1 8008026-0 1. of internal damping springs 76b, 77b, 78b acting para11e11t.

Regarding the operation of this embodiment, rotation of the piston plate 23b causes the drive tabs 114 to move and compress the springs 73b, which act on the dividing member 128 of the ring 122 to compress the springs 74b, which in turn act on the sliding dividing members 130 to compress the springs 75b, the springs 75b acting on the arms 139 to cause rotation of the drive member 137 relative to the drive ring or hub 146. Movement of the arms causes rotation of the drive tabs 143 to compress the springs 76b, which causes the slider to move. the springs 77b, which result in movement of the dividing elements 153 to compress the springs 78b and in turn cause rotation of the tabs 147 on the inner drive ring or hub 146 to rotate the turbine hub 19b. Thus, a damping effect of up to a maximum of 900 is achieved with these embodiments of the damper.

Claims (9)

8ÛÛ8Û26-Û '12 PATENTKRAV Two-stage torque vibration damper (10) for transmitting torque between driving and driven elements, comprising a piston plate (23) operatively connected to torque input means, at least two drive vanes (28) attached to the piston plate, a hub (92 ) operatively connected to an output shaft1 (22), characterized by at least two outer floating members (65, 68 or 103, 104) arranged to move in a cup-shaped path around the hub, at least two inner floating members (79, 81) arranged to move in a second arcuate path around the hub concentrically with the first arcuate path, four outer damping springs (73, 74, 75) movable in the first arcuate path, several inner damping springs (76, 77, 78) movable in the second arcuate path the web (28) having projections (28) extending inwardly into the first arcuate web and a rotatable member (32, 33) having at least two drive elements (41, 55) extending into the first arcuate web and at least two drivbyg1ar (44, 61) as st extends into the second arcuate path, the hub having at least two arms (97, 98) extending into the second arcuate path, and the outer damping springs being inserted between the outer floating means and the drive elements, and the internal damping springs are inserted between the drive shafts and the other floating means. Damping device according to claim 1, characterized in that the drive members (28) are axially aligned with the drive elements (41, 55) and that the hub arms (97, 97) are axially aligned with the drive members (44, 61) at from - the presence of imposed torque with the input means. 3. A damping device according to claim 2, characterized in that the outer floating means comprise a pair of dividing rings (65, 68) spaced on the intermediate element (32, 33) within each other, each dividing ring having at least two outwardly extending arms (66 or 11). 69) which divides the 13 aoosozs-o outer damping springs; the arms (66, 67) of each dividing ring are partially inwardly offset from the adjacent ring to be located in a common plane and wherein the inner floating means comprise two pairs of sliding dividing elements (79, 81) which separate the inner damping springs, which divide element slides on the intermediate element (32, 33). Damping device according to claim 2, characterized in that the intermediate element comprises a pair of irregularly shaped holding plates (32, 33) connected at intervals, that the drive elements (41, 55) and the drive brackets (44, 61) are formed in one piece with the plates and that the retaining plates (32, 33) have peripheral radial flanges (37, 52) spaced apart to receive the drive tabs (28) projecting into the outer arcuate path of the outer damping springs, that at least one retaining plate is mounted on the hub. Damping device according to claim 4, characterized in that the holding plates have outer arcuate grooves (45, 56) separated by the drive elements (41, 55) for receiving the outer damping springs and inner arcuate spring pockets (59) which receive the inner damping springs , that the drive brackets (44, 61) are displaced inwards into the pockets to extend into the path of the inner damping springs, and that the hub arms (97, 97) extend radially outwards from a hub sleeve (93) into the second arcuate path and between the inwardly displaced drive brackets (44, 6l). Damping device according to claim 2, characterized in that the outer floating means comprise at least two pairs of sliding dividing elements (l03, l04) slidable on the intermediate elements (32, 33) and separating the outer damping springs (73, 74, 75). ) and that the inner floating members comprise two pairs of sliding dividing elements (79, 81) separating the inner damping springs and that the intermediate element comprises a pair of irregularly shaped holding plates (32, 33) having peripheral radial flanges (37, 52) connected at intervals, that the drive elements (41, 55) and the drive brackets (44, 61) are integral therewith and that at least one holding plate (33) is mounted on the hub. Damping device (12) according to claim 2, characterized by a pair of oppositely arranged drive tabs (114) in which there are peripheral grooves (121), that the hub (146) has an annular flange (148) attached to the outlet means (19b) and which at the outer periphery abut in a ring (146), a pair of oppositely arranged hub arms (147) extending radially inwardly from the ring, the intermediate member (137) comprising a central ring (138) concentric with the hub ring and an inner ring (142) connected to the central ring (143) by means of the drive members, and that the drive member (139) extends outwardly from the central ring into the grooves (121) in the drive members (114). Damping device according to claim 7, characterized in that the hub ring (146) and the arms (147) have oppositely arranged elongate grooves (151) which receive the drive members (143) and that the drive members (114) comprise outer peripheral guide fins. (120) designed on these. Damping device according to claim 8, characterized in that the outer floating means comprise a dividing ring (122) having a hanging flange (126) and an annular guide groove (125) receiving the guide flanges (120) and a pair of oppositely arranged inwardly extending spring dividing elements (128) integral therewith and projecting into the outer arcuate web, a pair of oppositely arranged sliding dividing elements (130) movable on a guide surface (124) on the ring and further comprising two pairs of sliding dividing elements (152, 53) moving on the inner surface of the hub ring.