GB2183006A - Structure for supporting springs in a damper disc - Google Patents
Structure for supporting springs in a damper disc Download PDFInfo
- Publication number
- GB2183006A GB2183006A GB08626892A GB8626892A GB2183006A GB 2183006 A GB2183006 A GB 2183006A GB 08626892 A GB08626892 A GB 08626892A GB 8626892 A GB8626892 A GB 8626892A GB 2183006 A GB2183006 A GB 2183006A
- Authority
- GB
- United Kingdom
- Prior art keywords
- input
- spring
- side plates
- output part
- engagement means
- Prior art date
- Legal status (The legal status 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 status listed.)
- Granted
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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/22—Friction clutches with axially-movable clutching members
- F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
-
- 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
- F16F15/12353—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
- F16F15/1236—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
- F16F15/12366—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/60—Clutching elements
- F16D13/64—Clutch-plates; Clutch-lamellae
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
- F16D3/14—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions combined with a friction coupling for damping vibration or absorbing shock
Landscapes
- 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
A structure for supporting springs in a damper disc comprises an annular output part (2, 3); a pair of annular input parts (5, 8) disposed at opposite sides of the said output part (2, 3); first, second and third spring engagement portions (25, 26, 29, 30, 27, 28) spaced to each other and formed in said input parts and said output part; and first, second and third spring mechanisms (20, 21, 22) respectively, for circumferentially and elastically connecting the input part (5, 8) to the output part (2, 3). Said engagement portions are so designed that the first spring mechanism (20) may be supported by the first engagement portions (25, 26) in the input and output parts. The second spring mechanism (21) may be supported only by the second engagement portion (30) in the input parts and the third spring mechanism (22) may be supported only by the engagement portion (27) in the output part, in an initial condition. <IMAGE>
Description
SPECIFICATION
Structure for supporting springs in a damper disc
The present invention relates to a damper disc generally used as a clutch disc of a friction clutch, and more particularly to a structure for supporting springs in the damper disc.
In some of conventional damper discs, as described as a modified example in the U.S.
Patent No. 4,485,907 (Japanese Patent Application No.55-133812), flanges of hubs, which are output members, are circumferentially connected to side plates, which are input members, through three kinds (i.e., first, second and third) springs. In each of such discs, when the side plates do not torsionally turns relatively to the flange, i.e., in an initial condition, the first spring or springs are engaged with openings in the flange and the side plates, and the second and third springs are engaged and suppoted in the openings in the flange or the side plates. The first spring or springs are- compressed through the whole torsion operation. When a torsion angle between the side plates and the flange increases over a first predetermined value, the second springs are compressed. When the angle increases over a second predetermined value, the third springs are compressed.Thus, the torsion characteristics or damping characteristics change twice and have three stages in an operation in a positive direction, so that torque vibration can be absorbed effectively.
However, in the above conventional structure, all of the second and third springs are engaged with the edges of the openings of only the flange or only the the side plates, and are circumferentially spaced from the edges of the openings in the the side plate or the flange, in the initial condition.
Therefore, if the second and third springs are designed to be supported by the edges of the openings in the flange, in the initial condition, it is necessary to provide the circumferentially long openings in the side plates so that the second and third springs may not engage with the edges of those openings in the initial condition. These long openings reduce circumferential distances between the adjacent openings and between the openings and stop pins fixed to the side plates for limiting maximum torsion angle, which results in reduction of strength of the side plates. In other words, if it is intended to provide the sufficient strength in the side plates, it is difficult to form the long openings, and thus it is difficult to set the sufficiently large torsion angle for effectively absorbing the torque vibration.
If the side plates are designed to support the second and third springs in the openings therein, it is necessary to provide the circumferentially long openings in the flange to form spaces between the edges of the openings and the second and third springs in the initial condition. In this case, short distances are left between the adjacent openings and between the openings and recesses through which the stop pins extend, which results in weak structure of the flange. In other words, due to the necessity of providing the sufficient strength in the flange, it is difficult to set the sufficiently large torsion angle for effectively absorbing the torque vibration.
Accordingly, it in an object of the invention to provide an improved structure, overcoming the above-noted problems.
According to the invention, a structure for supporting springs in a damper disc comprises an annular output part; a pair of annular input parts disposed at opposite sides of the said output part; first, second and third spring engagemet means spaced to each other and formed in said input parts and said output part; and- first, second and third spring mechanisms disposed in the first, second and third spring engagement means, respectively, for circumferentially and elastically connecting the input part to the output part; said engagement means being so designed that the first spring mechanism may be supported by the first engagement means in the input and output parts, the second spring mechanism may be supported only by the second engagement means in the input parts and the third spring mechanism may be supported only by the engagement means in the output part, in an initial condition.
According to the anbove strcutre, when a torque is transmitted from the input parts to the output part, the first, second and third spring mechanisms are compressed, and thus, the input part torsionally turns or twists relatively to the output part.
While the torsion angle is smaller than the predetermined first value, only the first spring mechanism is compressed. Therefore, the torsion angle largely changes in accordance with a small change of the torque.
When the torsion angle increases over the predetermined first value, the second spring mechanism, which has been supported only by the engagement means in the input part, engages the engagement means in the output part, and is compressed. Thus, the rate of the change of the torsion angle with respect to the change of the torque decreases.
When the torsion angle increases over the predetermined second value, and third spring mechanism, which has been supported only by the engagement means in the output part, engages with the engagement means of the input part, and is compressed. Thus, the rate of the change of the torsion angle with respect to the change of the torque further decreases.
Other and further objects, features and advantages of the invention will appear more fully from the following description of the preferred embodiment of the invention.
Figure 1 is an elevation view of a clutch disc of an embodiment of the invention with certain part cut away;
Figure 2 is a sectional view taken along line Il-Il in Fig. 1.
Referring to Fig. 2, an output shaft 1, only a center line of which is shown, is splined to a hub 2 provided with radial flange 3. The hub 2 and the annular flange 3 form an output part. At opposite sides of the flange 3 are disposed a pair of annular side plates 5. A friction facing 7 is connected to an radially outer portion of one of the side plates 5 through cushioning plates 6. Annular subplates 8 are interposed between the flange 3 and the side plates 5, respectively. The side plates 5 and the sub-plates 8 form an input part.
A friction member 10 having small friction force is interposed between the radially inner portions of each sub-plate 8 and flange 3. A friction member 11 having large friction force is interposed between the radially inner portions of each sub-plate 8 and the side plate 5 adjacent thereto. These friction members 10 and 11 are formed by, e.g. friction plate, friction washer and/or wave spring. A cylindrical sleeve 12 is fitted around the outer periphery of a lefthand portion in Fig. 2 of the hub 2, and is fitted into the inner periphery of the side plate 5, sub-plate 8 and friction members
10 and 11.
Both of the side plates 5 are rigidly connected at the radially outer portions thereof by stop pins 15 which extend axially, i.e., are parallel to the output shaft 1. The flange 3 is provided at the radially outer portions with recesses 16 through which the stop pins 15 extend. Both of the sub-plates 8 are rigidly connected at the radially outer portions thereof by axially extending sub-pins 17, which extend through recesses 18 formed in the flange 3.
First torsion springs 20 (compressible coil springs) are disposed between the radially inner portions of the side plates 5. The springs 20 are located in the openings 25 formed in the flange 3, and are seated at the ends thereof on spring seats 23, respectively. Each spring seat 23 is provided with projections 24, which project in axially opposite directions into openings 26 formed in the sub-plates 8.
Third springs 22 (compressible coil springs) are disposed between the radially outer portions of the side plates 5. The springs 22 are located in openings 27 formed in the flange 3.
Both side plates 5 are provided with concave portions or hollows 28, in which the springs 22 are partially received.
Referring to Fig. 1, said springs 20 and 22 are three in number, and are disposed in tangentail direction of the disc with circumferential spaces therebetween, respectively. Three second spring sets 21 are also disposed at the radially outer portion of the disc. Each spring sets 21 inlcudes coaxially arranged two compressible coil springs having small and large diameters and extend in the tangential direction of the disc, respectively. The spring set 21 and said springs 22 are alternately arranged in the disc with circumferential spaces therebetween. The flange 3 and the side plates 5 are provided with openings 29 and 30 in which the spring sets 21 are loacated, respectively.
In an initial or non-torsion condition illustrated in Fig. 1, each members and portions are in following condition. The spring seats 23 at both ends of each spring 20 are engaged with edges of the openings 25 and 26 in the flange 3 and the sub-plates 8. Both ends of each spring 22 are engaged only with edges of the opening 27 in the flange 3, and are circumferentially spaced from end walls 31 of the hollows 28 in the side plates 5 with circumferential spaces N and n corresponding to positive and negative second torsion angles (e.g., +16.5 and -7.5 degrees), therebetween. Both ends of each spring sets 21 are engaged only with edges of the openings 30 in the side plates 5, and are circumferentially spaced from edges of the opening 29 in the flange 3 with circumferential spaces M and m corresponding to positive and negative first torsion angles (e.g., +11 and -5 degrees) therebetween.
Further, in the initial condition, each stop pin 15 is circumferentially spaced from edges of the recess 16 with spaces S and s corresponding to positive and negative maximum torsion angles (e.g., +18 and -9 degrees) therebetween. Each sub-pin 17 is circumferentially spaced from edges of the recess 18 with spaces Q and q, which are slightly larger than said first tortion angles, therebetween.
An operation is as follows. When the facing 7 is pressed onto a flywheel (not illustrated) by an appropriate mechanism (not illustraed), a torque is transmitted from the flywheel through the facing 7 to the side plates 5. The torque is then transmitted from the side plates 5 though the spring 20, 21 and 22 to the flange 3, and is transmitted therefrom through the hub 2 to the output shaft 1. In this operation. The springs 20, 21 and 22 are compressed by a force corresponding to the transmitted torque, so that the side plates 5 and the sub-plates 8 torsionally turn or twist relatively to the flange 3.
In the above operation, when the transmitted torque is small, the side plates 5 and the sub-plates 8 are unrotatably connected by the friction force of the friction members 11. Thus, when the torque is small, i.e., the torsion angle is below the predetermined first value, only the springs 20 are compressed between the sub-plate 8 and the flange 3. Therefore, the torsion angle changes largely in accordance with small change df the transmitted torque. Further, in this first operation stage, frictional sliding occurs only on the surfaces of the friction members 10, so that small hysteresisis is generated in the twisting or damping characteristics.
When the torsion angle increases over the predetermined first value, i.e., in a second operation stage, the spring sets 21, which have been supported only by the edges of the openings 30 in the side plates 5, engage the edges of the openings 29 in the flange 3, and are compressed. Therefore, the rate of change of the torsion angle with respect to the change of the transmitted torque decreases.
When the torsion angle increases over the predetermined second value, i.e., in a third operation stage, the springs 22, which have been supported only by the edges of the openings 27 in the flange 3, engage with the end walls 31 of the hollows 28 in the side plates 5, and are compressed. Therefore, the rate of change of the torsion angle with respect to the change of the transmitted torque further decreases.
In said second and third operation stages, the sub-pins 17 engage the recesses 18, so that the sub-plates 8 are unrotatably connected to the flange 3. Thus, the side plates 5 twist relatively to the sub-plates 8, and thus, sliding occurs on the surfaces of the friction members 11, so that large hysteresis is caused by the friction on the members 11 in the damping characteristics.
When the torsion angle increases to the maximum value, the stop pins 15 engage the edges of the recesses 16, so that any further twisting is prevented.
According to the invetion, as described hereinbefore, the total ciricumfrential lenght of the openings 29 and 27 (i.e., spring engagement means) formed in the flange 3 for the second and third springs 21 and 22 is longer than the total length of the springs 21 and 22 in the initial condition only by a length corresponding to a sum of the lengthes of the spaces M and m, i.e., of the positive and negative first torsion angles. Further, the total ciricumfrential lenght of the openings 30 and hollows 28 (i.e., spring engagement means) formed in the side plates 5 for the second and third springs 21 and 22 is longer than the total length of the springs 21 and 22 in the initial condition only by a length corresponding to a sum of the lengthes of the spaces N and n, i.e., of the positive and negative second torsion angles.
Therefore, as compared with the conventional structure in which only the flange 3 or only the side plates 5 are provided with both of the spaces M and m and spaces N and n corresponding to the first and second torsion angles, respectively, the lengthes of the openings and hollows in the flange 3 and the side plates 5 can be short, and thus, the strength thereof can be increased. In other words, the openings and/or hollows can be long enough to obtain desired maximum torsion angle without reducing the strength, so that the torque vibration can be absorbed effectively.
In the illustrated embodiment described above, the third springs 22 supported by the flange 3 are designed to operate only the third operation stage, and the second spring sets 21 supported by the side plates 5 are designed to start to operate in the second operation stage. However, the spaces M and m may be formed longer than the spaces N and n, respectively, so that the third springs 22 may start to operate in the second operation stage, and the second spring sets 21 may operate only in the third operation stage.
Although the invention has been described in its preferred form with a certain degree of particularity, it is understood that the structure of the preferred form may be changed in the details of construction, and that the combination and arrangement of parts may be modified to without departing from the spirit and scope of the invention as hereinafter claimed.
Claims (5)
1. A structure for supporting springs in a damper disc comprising; an annular output part; a pair of annular input parts disposed at opposite sides of the said output part; first, second and third spring engagemet means spaced to each other and formed in said input parts and said output part; and first, second and third spring mechanisms disposed in the first, second and third spring engagement means, respectively, for circumferentially and elastically connecting the input part to the output part; said engagment means being so designed that the first spring mechanism may be supported by the first engagement means in the input and output parts, the second spring mechanism may be supported only by the second engagement means in the input parts and the third spring mechanism may be supported only by the engagement means in the output part, in an initial condition.
2. A structure of claim 1 wherein said first spring mechanism includes a plurality of circumferentially spaced first springs which are arranged in radially inner portions of the input and output parts, and said second and third spring mechanisms include a plurality of circumferentially spaced springs which are arranged in radially outer portions of the input and output parts.
3. A structure of claim 1 wherein said output part includes a radial flange formed on a hub which is connected to an output shaft, and said input parts include a pair of side plates disposed at opposite sides of said flange and sub-plates frictionally connected to the side plates and disposed between the flange and the side plates, respectively.
4. A structure of claim 3 wherein said first engagement means of the input parts is openings formed in the sub-plates, said second engagement means in the input parts is openings formed in the side plates, said third engagement means in the input parts is hollows formed in the side plates, and said first, second and third engagement means in the output part are openings formed in the fange.
5. A structure for supporting springs a damper disc substantially as hereinbefore described with reference to and as illustrated in the accompanying drawings.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60257164A JPH0758107B2 (en) | 1985-11-15 | 1985-11-15 | Damper disc spring support structure |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| GB8626892D0 GB8626892D0 (en) | 1986-12-10 |
| GB2183006A true GB2183006A (en) | 1987-05-28 |
| GB2183006B GB2183006B (en) | 1990-09-12 |
Family
ID=17302584
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB8626892A Expired - Lifetime GB2183006B (en) | 1985-11-15 | 1986-11-11 | Structure for supporting springs in a damper disc |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPH0758107B2 (en) |
| KR (1) | KR920008169B1 (en) |
| DE (1) | DE3638938A1 (en) |
| FR (1) | FR2591697B1 (en) |
| GB (1) | GB2183006B (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2735548A1 (en) * | 1995-06-19 | 1996-12-20 | Valeo | TORSION DAMPING DEVICE |
| US6712705B2 (en) * | 2001-01-18 | 2004-03-30 | Exedy Corporation | Damper mechanism |
| CN105485200A (en) * | 2016-01-15 | 2016-04-13 | 中国重汽集团济南动力有限公司 | Clutch driven disc used for commercial vehicle |
| CN107339333A (en) * | 2016-12-28 | 2017-11-10 | 安徽江淮汽车集团股份有限公司 | A kind of clutch driven plate vibration-proof structure |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19536513C2 (en) * | 1994-09-29 | 2002-02-14 | Exedy Corp | Vibration damper for a disc clutch |
| JP3732021B2 (en) | 1998-09-18 | 2006-01-05 | 株式会社エクセディ | Damper mechanism |
| FR2976331B1 (en) * | 2011-06-07 | 2013-05-24 | Valeo Embrayages | TORSION DAMPING DEVICE, IN PARTICULAR FOR TRANSMISSION OF MOTOR VEHICLE |
| CN112855798B (en) * | 2021-03-03 | 2023-01-03 | 舍弗勒技术股份两合公司 | Torque limiting device, torque transmission device, and vehicle |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2293781A (en) * | 1939-07-22 | 1942-08-25 | Thelander W Vincent | Friction clutch plate |
| FR77424E (en) * | 1960-03-29 | 1962-03-02 | Ferodo Sa | Motor vehicle transmissions improvements |
| FR1525291A (en) * | 1967-04-05 | 1968-05-17 | Ferodo Sa | Improvements to damper hub clutch friction |
| FR2162702A5 (en) * | 1971-11-29 | 1973-07-20 | Ferodo Sa | |
| JPS57134019A (en) * | 1981-02-13 | 1982-08-19 | Daikin Mfg Co Ltd | Clutch disc |
| FR2507720A1 (en) * | 1981-06-16 | 1982-12-17 | Automotive Prod France | FRICTION CLUTCH OUTPUT DISC |
| JPS58196324A (en) * | 1982-05-13 | 1983-11-15 | Aisin Seiki Co Ltd | Clutch disc |
| US4618048A (en) * | 1982-06-29 | 1986-10-21 | Aisin Seiki Kabushiki Kaisha | Clutch disk assembly |
| DE3230663C2 (en) * | 1982-08-18 | 1986-02-27 | Fichtel & Sachs Ag, 8720 Schweinfurt | Clutch disc with torsional vibration damper and control plate |
| JPS5962725A (en) * | 1982-09-30 | 1984-04-10 | Aisin Seiki Co Ltd | Frictional type engaging disc device |
| JPS60112727U (en) * | 1984-01-05 | 1985-07-30 | 株式会社 大金製作所 | damper disc |
| DE3415927A1 (en) * | 1984-04-28 | 1985-10-31 | Fichtel & Sachs Ag, 8720 Schweinfurt | Torsional vibration damper with idle suspension that can be loaded in both directions of rotation |
| JPS6141019A (en) * | 1984-07-31 | 1986-02-27 | Daikin Mfg Co Ltd | Damper disc |
-
1985
- 1985-11-15 JP JP60257164A patent/JPH0758107B2/en not_active Expired - Lifetime
-
1986
- 1986-11-11 GB GB8626892A patent/GB2183006B/en not_active Expired - Lifetime
- 1986-11-12 KR KR1019860009520A patent/KR920008169B1/en not_active IP Right Cessation
- 1986-11-14 FR FR8615845A patent/FR2591697B1/en not_active Expired
- 1986-11-14 DE DE19863638938 patent/DE3638938A1/en not_active Ceased
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2735548A1 (en) * | 1995-06-19 | 1996-12-20 | Valeo | TORSION DAMPING DEVICE |
| WO1997000390A1 (en) * | 1995-06-19 | 1997-01-03 | Valeo | Torsion damping device |
| US5885160A (en) * | 1995-06-19 | 1999-03-23 | Valeo | Torsion damping device having circumferentially acting resilient members of different stiffness |
| US6712705B2 (en) * | 2001-01-18 | 2004-03-30 | Exedy Corporation | Damper mechanism |
| CN105485200A (en) * | 2016-01-15 | 2016-04-13 | 中国重汽集团济南动力有限公司 | Clutch driven disc used for commercial vehicle |
| CN107339333A (en) * | 2016-12-28 | 2017-11-10 | 安徽江淮汽车集团股份有限公司 | A kind of clutch driven plate vibration-proof structure |
Also Published As
| Publication number | Publication date |
|---|---|
| FR2591697B1 (en) | 1989-11-17 |
| FR2591697A1 (en) | 1987-06-19 |
| GB2183006B (en) | 1990-09-12 |
| KR920008169B1 (en) | 1992-09-24 |
| GB8626892D0 (en) | 1986-12-10 |
| DE3638938A1 (en) | 1987-05-21 |
| JPH0758107B2 (en) | 1995-06-21 |
| JPS62118122A (en) | 1987-05-29 |
| KR870005194A (en) | 1987-06-05 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PCNP | Patent ceased through non-payment of renewal fee |
Effective date: 19931111 |