WO1988003622A1 - Amortisseur de verrouillage pour convertisseurs de couple - Google Patents

Amortisseur de verrouillage pour convertisseurs de couple Download PDF

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Publication number
WO1988003622A1
WO1988003622A1 PCT/JP1987/000799 JP8700799W WO8803622A1 WO 1988003622 A1 WO1988003622 A1 WO 1988003622A1 JP 8700799 W JP8700799 W JP 8700799W WO 8803622 A1 WO8803622 A1 WO 8803622A1
Authority
WO
WIPO (PCT)
Prior art keywords
rim
spring
damper
drive ring
turbine
Prior art date
Application number
PCT/JP1987/000799
Other languages
English (en)
Japanese (ja)
Inventor
Masahiko Koshimo
Original Assignee
Kabushiki Kaisha Daikin Seisakusho
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kabushiki Kaisha Daikin Seisakusho filed Critical Kabushiki Kaisha Daikin Seisakusho
Publication of WO1988003622A1 publication Critical patent/WO1988003622A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/1232—Wound springs characterised by the spring mounting
    • F16F15/1234—Additional guiding means for springs, e.g. for support along the body of springs that extend circumferentially over a significant length
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/1232—Wound springs characterised by the spring mounting
    • F16F15/12326—End-caps for springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0294—Single disk type lock-up clutch, i.e. using a single disc engaged between friction members

Definitions

  • the present invention relates to a torque converter, wherein when a lock-up clutch for disengaging a torque converter (lock-up) is operated, torsional vibration generated in an engine is transmitted to a subsequent transmission.
  • the present invention relates to a lock-up damper device provided between a piston (clutch plate) of a lock-up clutch and a turbine of a torque converter in order to prevent transmission to the side.
  • FIGS. 14 and 15 show the main parts of U.S. Pat. No. 4,240,532, and FIGS. 16 and 17 show the main parts of Japanese Utility Model Publication No. 61-28i26.
  • the lock-up damper 100 is located between the torque converter body 101 and the front cover 102, and the front cover 102 is located between the pump 103 and the part 104. It is welded and connected to the input shaft 114 at the outer joint 1 ⁇ 6.
  • 107 is a turbine
  • 108 is a stator
  • turbine 107 and hub 109 are connected by rivet 110
  • hub 1 ⁇ 9 is spline-fitted to output shaft 115 .
  • the stator 108 is spline-fitted to the fixed cylinder shaft 1 16 at the central portion of the inner race 1 112 of the one-way clutch 111.
  • the mouthpiece damper 100 is welded to the piston (clutch ⁇ ) 117 supported movably in the axial direction with respect to the hub 109 and to the rear (right side) of the outer periphery of the clutch plate 117.
  • the driven ring 122 is fixed to the turbine 107.
  • a friction facing 1 2 3 is fixed to the front of the outer periphery of the clutch ⁇ 1 17, and the facing 1 2 3 of the clutch ⁇ 1 17 is located at the front due to the pressure difference between the front and back of the clutch ⁇ 1 17.
  • the front cover 1 ⁇ 2 is directly connected (locked up) to the turbine 107 via the damper spring 120 of the mouth lock damper 100. .
  • the drive ring 1 18 in FIG. 14 includes an outer peripheral rim 1 2 5, a support wall 1 2 6, and a spring accommodating section 1 19 for forming the spring accommodating section 1 19.
  • Protrusions 127 and protruding wall portions 128 are integrally formed on both sides to form spring supports, and a long damper spring 120 and a short damper spring 120a form a set to accommodate one spring.
  • the claw part 121 is accommodated in the part 119, and the claw part 121 is arranged between both springs 120 and 120a.
  • both springs are pressed against the outer peripheral rim of drive ring 125 by strong force due to the centrifugal force of the springs 12 ⁇ and 12 ⁇ a.
  • both springs 120, 120 a Both snaps 120 and 120a move axially with respect to the drive ring 1 18 together with the claw 1 21 when the clutch is ON and OFF because the snap fit is on the claw 1 2 1 As a result, the smooth movement is hindered by the large frictional resistance between the springs 120 and 120a and the outer peripheral rim 125, and the operation of the clutch is not smooth.
  • a separate drive ring 1 18 is fixed to the clutch ⁇ 1 17 as shown in Fig. 14a, and the tip edge of the outer rim 1 25 of the drive ring 1 18 is moved inward in the radial direction. It is also conceivable to form a stopper portion 125a that bends to prevent the damper spring 120 from moving in the axial direction. By providing a sloped part 125a at the tip of the outer rim 125, the strength of the outer rim 125 can be significantly improved and the thickness can be reduced. it can. However, since the centrifugal force of the damper spring 120 must be received only by the drive ring 118, there is a limit to the reduction in sheet thickness. In the device shown in FIGS.
  • the clutch ⁇ 117 An outer peripheral rim 1 17a for directly receiving one spring 12 ° is integrally formed, and a plurality of springs for receiving the end face of the damper spring 120 on the outer peripheral back of the clutch ⁇ 117. Receiver 130 is fastened by rivet 13 1.
  • the spring support 13 ⁇ has a support wall 13 1 integrally.
  • Reference numeral 132 in FIG. 17 denotes a spring seat.
  • the clutch receives the centrifugal force of the damper spring 12 ⁇ at high speeds.
  • the outer rim 1 117a of 117 is easily deformed due to its structure, and a thick plate must be used to withstand the rotational stress. Cost increases.
  • An object of the present invention is to provide a new structure lock-up damper device which avoids all the above-mentioned conventional problems, has a reliable clutch function and a damper function, has a simpler structure, is easier to assemble, and has a lower itf. .
  • the turbine of the torque converter body ⁇ is connected to the pump on the opposite side and the front cover for connecting the pump to the input shaft on the other side.
  • a clutch ⁇ frictionally engaged with the front cover is provided between the turbine and the front cover so as to be movable in the axial direction, and the clutch plate and the turbine are circumferentially moved.
  • the clutch plates are connected to each other via a plurality of longitudinal damper springs so that they can rotate relative to each other.
  • a sheet metal drive ring is fixed to the outer peripheral portion of the clutch plate on the turbine side, and the damper springs are radially outer and inner sides of the drive ring.
  • Claw portions extending from the turbine-side driven ring are arranged in the spring receiver, and the tip of the rim is provided. ⁇ is bent radially inward to form a part of the stopper that prevents the damper spring from moving in the axial direction.
  • An eave that covers the rim of the drive ring from the outside is provided with a slight gap between the rim and the eaves, extending at least to the boundary between the rim of the drive ring and a part of the stopper. The gap is made small enough that the eaves can reinforce the rim when deformed.
  • FIG. 1 is a partially cutaway rear view of the driven ring with half removed, and Fig. 2 is the ⁇ -! [A longitudinal side view along the line, FIG. 3 is a longitudinal side view along the line III-HI of FIG. 1, FIG. 4 is a partial rear view of the drive ring, FIG. 5 is a perspective view of the same, FIG. rear view of a single drive ring, FIG. 7 is W- VII sectional view of FIG. 6, FIG. 8 is 1 VI- 1 1 cross-sectional view of FIG. 6, FIG. 9 is a rear partial view of the driven-ring FIG. 10 is a longitudinal side view of a driven ring, FIG. 11 is a perspective view showing a damper spring and a spring seat, and FIG.
  • FIG. 12 is a longitudinal view of a torque converter incorporating a device according to the present invention.
  • Cross section, Fig. 12A is another implementation ⁇ Drawing corresponding to FIG. 12 to show FIG. 13,
  • FIG. 13 is a graph showing the operation
  • FIG. 14A is a partial longitudinal sectional view showing a conventional example
  • FIG. Fig. 14 is a partial sectional view taken along the line XV-XV of Fig. 14, and
  • Figs. 16 and 17 are drawings corresponding to Figs. 14 and 15 for showing another conventional example.
  • the lock-up damper device includes a gold drive plate 13 fixed to a lock-up clutch piston 11 (clutch ⁇ ) by a rivet 12.
  • a driven plate 14 fixed by rivets (both not shown) to the evening bin of the torque converter, and an outer peripheral portion of the plate disposed between these plates 13 and 14 Two different damper springs 15 and 16 are provided.
  • the drive plate 13 has an outer peripheral rim 13 a along the inner surface of the outer peripheral rim 11 a of the piston 11, and the rim 13 a has a height, as viewed in the damper axial direction, of the piston 11 1. It is slightly larger than the height of the rim 11a.
  • a series of support walls 17 located on the drive plate 13 facing the rim 13a from the inside in the radial direction (radial direction) are intermittently arranged on the same circumference. Each of these support wall portions 17 forms cuts corresponding to the three sides of the window hole 18 in the drive plate 13, and cuts and raises the support wall portion 17 along the cuts to form the drive plate 1.
  • a window hole 18 having a shape corresponding to the support wall portion 17 is left outside of the support wall portion 17 in the radial direction.
  • Each of the damper springs 15 and 16 is installed in a posture extending in the circumferential direction in the spring accommodating portion 19 formed between the outer peripheral rim 13 a and each of the supporting wall portions 17 slightly lower than the outer rim 13 a, and is disposed radially outward. Inward and inward shedding are prevented. Further, the tip ⁇ of the outer peripheral rim 13 a is curved inward in the radial direction to form a stopper 13 b. That is, as is clear from the enlarged view attached to FIG. 3, the stopper 13 b is fitted into the outer peripheral rim 11 a (eave) of the piston 11 with a slight gap, and the outer peripheral rim 11 b.
  • a cylindrical outer rim 13a is partially connected to a partially tapered stopper 13b. It has a three-dimensional structure with a gun.
  • the stopper 13b generally follows the shape of the damper springs 16 and 15 on the inner side in the radial direction, and accordingly, the damper-the spring 16 and 15 dampers when the springs 16 and 15 are extended radially outward by centrifugal force. It receives the centrifugal force from the springs 16 and 15 and comes into contact with the inner surface of the piston rim 11a, and the contacts gradually move outward in the axial direction (to the right in Fig.
  • the eaves 11a in Fig. 3 protrude beyond the boundary P between the outer peripheral rim 13a of the drive ring 13 and the stopper 13b by the dimension a.
  • the dimension between the boundaries P is preferably 0 or more at worst tolerance.
  • the gap is kept within a dimension (0.5 ram if it is cold) that allows elastic deformation of the rim 13 a of the drive ring 13 where crack growth does not start.
  • the mechanism of destruction of the drive ring 13 due to the centrifugal force of the spring is that the cylindrical outer rim 13 a undergoes elastic deformation, and cuts and raises between the outer peripheral rim 13 a and the spring receiving protrusion 21 b to cause a crack to develop at the root. It was found that the rotational strength was improved by suppressing the deformation of the boundary P. That is, as shown in Fig. 3, it is possible to take countermeasures by extending the outer rim (eave) 1 la of the clutch # 11 longer than the boundary P (different dimensions). ⁇ Dimensions must be within the allowable dimensions of elastic deformation where crack propagation does not start, as described above.
  • the driving plate 13 has a pair of protrusions 2 1 facing each other from the outside in the radial direction with respect to the respective projecting wall portions 20 which are located slightly outside in the radial direction from the supporting wall portions 17.
  • a and 2 IB are intermittently provided on the same circumference so that the projecting wall portion 20 and the projections 21 A and 21 B are located beside the spring accommodating portion 19.
  • a cut of a corresponding shape is formed in the main body of the drive plate 13 in each of the projecting wall portions 2, and a part of the drive plate 13 (a portion of the cut ⁇ ) is approximately 90 along the cut. It is formed integrally with the drive plate 13 by bending, so that the radial direction of each projecting wall portion 20!
  • a correspondingly shaped window hole 22 is left on the 3 ⁇ 4 side.
  • a pair of projections 21A and 21B form a notch in the middle in the axial direction and a pair of notches on the outer peripheral rim 13a, and between the notch and each notch, the outer periphery: the rim
  • the drive plate 13 is formed integrally with the drive plate 13 by bending 13a radially inward by about 90 °.
  • a series of projections 23 (claws) projecting in the direction of the drive ring 13 are formed on the outer peripheral end of the driven ring 14 at equal intervals on the same circumference on the driven ring 14 and the body. I have.
  • Each claw portion 23 is provided so as to enter between the protruding wall portion 20 of the drive ring 13 and the protrusions 21 A and 2 IB on the outside thereof when viewed in the radial direction of the damper.
  • the springs 15 and 16 are coil springs, and two pairs of long springs 15 are arranged adjacent to each other when viewed in the circumferential direction of the damper. It consists of a short spring 16 located between the pair. Spring seats 24 are fitted and held at both ends of each of the springs 15 and 16.
  • Each spring 24 has a leg 24a that fits within the end of the spring, and the end face 15a of each spring is in good contact with the spring seat 24, as shown in Figure 11 So that it is polished.
  • the spring accommodating portion 19 formed in the drive ring 13 is configured such that the sight of the tongue in the circumferential direction is large for the accommodating portion for the long spring 15 and small for the accommodating portion for the short spring 16.
  • the projecting wall portion 2 ⁇ of the force driving ring 13 and the projections 21A and 21B are provided in the following ⁇ .
  • the springs 15 and 16 are fitted with spring seats 24 at both ends and fitted into the respective spring accommodating portions 19 of the drive ring 13 as shown in the left half of FIG. With the springs 15 and 16 slightly compressed, the spring seats 24 at both ends are in contact with the projecting wall portions 20 and the projections 21A and 21B on both sides.
  • the drive ring 13 is combined with the springs 15 and 16 and the spring seat 24 as described above, and then the drive ring 13 is combined with the driven ring 14, the right half of FIG. 1 is obtained.
  • the spring seat 24 at the end of the long spring 15 comes into contact with the claw 23 of the driven ring 14 so that there is no play, whereas the end of the short spring 16 Between the spring seat 24 and the claw 23 of the driven ring 14 so that a play gap with a space da is left at one end in the circumferential direction, and a play space with a space db is left at the other end.
  • a projecting wall portion 20 of the ring 13 and projections 21A and 21B are provided.
  • the forward direction of the damper is the direction of arrow A in Fig. 1, while the distance da in the forward direction is larger than the distance db in the reverse direction (da> db). Is set.
  • the protruding wall portion retreats in the circumferential direction with respect to the projection so that the center portion of the damper spring becomes closer to a straight line rather than a convex portion at the time of stop or low rotation.
  • the spring seat 24 is separated from the protruding wall portion 2 by the gap L, and the spring seat 2 A gap is formed between the drive ring 4 and the drive ring claw 23, and the piston 11 including the drive ring with respect to the claw 23 becomes easy to move in the pulling direction.
  • a fusing 25 is fixed to the entire outer peripheral portion of the piston.
  • a hole 26 formed in the drive ring 13 for allowing the rivet 12 to pass therethrough is provided on the inner periphery of the drive ring 13 in a convex shape provided intermittently on the same circumference.
  • a hole 27 for passing a rivet for fixing the driven ring 14 to the converter turbine is formed in an inner peripheral portion of the driven ring 14.
  • the driven ring 14 is formed with circular window holes 28 at equal intervals for weight reduction.
  • the protruding wall 2 ⁇ ⁇ ⁇ of the drive ring 13 and the protrusion 21A located on the forward rotation side form one end of the long spring 15
  • the long spring 15 is compressed in the direction of the arrow A in FIG. 1 through the spring seat 24 of the driven spring 14, and the driven spring 14 is moved through the spring seat 24 at the other end of the long spring 15.
  • the rotation of the drive ring 13 is transmitted to the driven ring 14 by pushing the claw portion 23 in the direction of arrow A in FIG. After the long spring 15 is reduced by an amount corresponding to the distance da shown in FIG.
  • the protruding wall portion 20 of the drive ring 13 and the -projection 21 A are connected to one end of the short spring 16.
  • the short spring 16 When the short spring 16 is engaged with the spring seat 24, the short spring 16 is compressed in the direction of the arrow A in FIG. 1 through the spring seat 24, whereby the short spring 16 is compressed via the other end of the spring seat 24. Since the claw portion 23 of the drive ring 14 is pushed in the direction of arrow A, the short spring 16 also contributes to the transmission of rotational torque (two-step characteristic). The same applies when the lock-up clutch is connected while the engine is loaded in the reverse direction, with the drive ring 13 involved in the compression of the damper springs 15 and 16 and thus the transmission of torque. The projection only replaces the projection 21 A on the reverse side.
  • Fig. 13 shows the drive ring in the operating state of the device to which the present invention is applied.
  • the damper springs 15 and 16 fitted into the spring accommodating portion 19 of the drive ring 13 support the rim 13 a of the drive ring 13.
  • the wall 17 prevents the falling off in the radial direction, and is snap-fitted between the protruding wall 20 of the drive ring 13 and the protrusions 21A, 21B. It is not necessary to manually set the damper springs 15 and 16 when assembling with the driven ring 14.
  • the driven ring 14 can also be welded to the shell 107A of the turbine 107, as shown in FIG. 12A. In this case, space saving effect is produced
  • the lock-up damper device according to the present invention is useful when employed in a torque converter for an automobile or the like.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

Un anneau d'entraînement (13) est fixé sur un plateau d'embrayage (11) dans un embrayage à verrouillage, et est pourvu d'un siège de ressort, d'un rebord (13a) et d'une paroi de support (17) entre lesquels des ressorts amortisseurs (15, 16) sont maintenus dans le sens radial de l'anneau (13). Les parties de griffes (23) d'un anneau entraîné (14) sont disposées sur le siège de ressort. L'extrémité libre du rebord (13a) est courbée radialement vers l'intérieur pour former une butée (13b) pour les ressorts amortisseurs. L'extrémité de base de la butée (13b) est disposée à un endroit qui se trouve sur le côté radialement interne de saillies cylindriques (11a) formées dans la partie circonférentielle externe du plateau d'embrayage (11), et qui ne se trouve pas sur le côté axialement externe de ces mêmes saillies (11a).
PCT/JP1987/000799 1986-11-06 1987-10-16 Amortisseur de verrouillage pour convertisseurs de couple WO1988003622A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP17059486U JPS6375656U (fr) 1986-11-06 1986-11-06
JP61/170594U 1986-11-06

Publications (1)

Publication Number Publication Date
WO1988003622A1 true WO1988003622A1 (fr) 1988-05-19

Family

ID=15907733

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP1987/000799 WO1988003622A1 (fr) 1986-11-06 1987-10-16 Amortisseur de verrouillage pour convertisseurs de couple

Country Status (2)

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JP (1) JPS6375656U (fr)
WO (1) WO1988003622A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2254397A (en) * 1991-03-22 1992-10-07 Valeo A lock-up clutch for a hydrokinetic transmission.
CN112879523A (zh) * 2019-11-29 2021-06-01 上海汽车集团股份有限公司 液力变矩器总成
CN113719552A (zh) * 2021-08-12 2021-11-30 陕西航天动力高科技股份有限公司 一种离合器总成

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6128126Y2 (fr) * 1982-06-21 1986-08-21

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5997360A (ja) * 1982-11-22 1984-06-05 Honda Motor Co Ltd 流体トルクコンバ−タ用クラツチの作動制御装置

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6128126Y2 (fr) * 1982-06-21 1986-08-21

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2254397A (en) * 1991-03-22 1992-10-07 Valeo A lock-up clutch for a hydrokinetic transmission.
US5195622A (en) * 1991-03-22 1993-03-23 Valeo Lock-up clutch for a hydrokinetic power transmission apparatus for a motor vehicle
GB2254397B (en) * 1991-03-22 1994-11-16 Valeo A lock-up clutch for a hydrokinetic power transmission apparatus for a motor vehicle
CN112879523A (zh) * 2019-11-29 2021-06-01 上海汽车集团股份有限公司 液力变矩器总成
CN113719552A (zh) * 2021-08-12 2021-11-30 陕西航天动力高科技股份有限公司 一种离合器总成

Also Published As

Publication number Publication date
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