GB2188111A - Antilock braking system - Google Patents
Antilock braking system Download PDFInfo
- Publication number
- GB2188111A GB2188111A GB08705039A GB8705039A GB2188111A GB 2188111 A GB2188111 A GB 2188111A GB 08705039 A GB08705039 A GB 08705039A GB 8705039 A GB8705039 A GB 8705039A GB 2188111 A GB2188111 A GB 2188111A
- Authority
- GB
- United Kingdom
- Prior art keywords
- motor
- valve
- operating member
- hydraulic pressure
- braking system
- 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
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
- B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
- B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
- B60T8/42—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having expanding chambers for controlling pressure, i.e. closed systems
- B60T8/4208—Debooster systems
- B60T8/4266—Debooster systems having an electro-mechanically actuated expansion unit, e.g. solenoid, electric motor, piezo stack
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Regulating Braking Force (AREA)
Abstract
An antilock braking system includes a modulator 3 operatively interposed between a master cylinder 2 and a brake 1 associated with a wheel W. The modulator includes an output hydraulic pressure chamber 18 connected to the brake, a valve 19 operates to open and close communication between the said master cylinder and the said output hydraulic pressure chamber. Movement of an operating member 45 in a valve closing direction is arranged to cause an increase in the volume of the said output hydraulic pressure chamber. A rotational motor 49 is mounted to the modulator for driving the said operating member. A controller 50 operates the motor in response to a state in which the wheel is about to lock, and transmission means 53 between the motor and the operating member converts rotational motion of the motor into linear motion of the operating member. <IMAGE>
Description
SPECIFICATION
Antilock braking system
This invention relates to an anti-lock braking system.
Such a system is known in which, between an output port of a master cylinder and a brake associated with a wheel, there is interposed a modulatorwhich includes an output hydraulic pressure chamber connected to the brake, an opening and closing valve arranged to provide for communication and interruption as between said master cylinder output port and said output hydraulic pressure chamber, and an operating member operative to close the said opening and closing valve in response to a state in which the wheel is about to lock, the said operating member causing the volume ofthe output hydraulic chamberto increase upon such operation thereof.
In one known antilock braking system ofthis kind, hydraulic pressure generated in a hydraulic pressure actuator is controlled by a solenoid valve and then supplied to the modulatorto actuate the said operating member. It has been found, however, that the responsiveness ofthis known system is not wholly satisfactory, and furthermore the hydraulic pressure circuit is unduly complicated, with an undesirably large number of parts.
According to the present invention there is provided an antilock braking system including a modulator operatively interposed between a master cylinder and a brake associated with a wheel, the said modulator including an output hydraulic pressure chamber connected to the brake, a valve operative to open and close communication between the said master cylinder and the said output hydraulic pressure chamber, an operating member for the said valve, movement of the said operating member in a valve closing direction being arranged to cause an increase in thy volume of the said output hydraulic pressure chamber, a rotational motor mounted to the said modulatorfordriving the said operating member, means for operating the motor in response to a state in which the wheel is about to lock, and transmission means between the motor and the operating member arranged to convert rotational motion ofthe motor into linear motion of the operating member.
With such an arrangement, when the wheel is aboutto lock, the rotational motor is rotationally operated, in response to which the operating member moves linearlyto causeclosure ofthe said valve, and atthe same time the volume of the output hydraulic pressure chamber increases. As a result the braking hydraulic pressure acting on the brake reduces, thus preventing the wheel from locking.
An embodimentofthe invention will now be described by way of example and with reference to the accompanying drawing, which is a diagrammatic illustration of a system according to the invention, including an axial cross-sectional view of the modulatorforming part thereof.
Referring to the drawing, in a motor-cycle a pair of left and right disk brakes 1,1 are mounted on awheel W,thefrontwheelforexample,and hydraulic pressure output from a master cylinder 2 is supplied to both ofthe disk brakes 1, 1 through a modulator3.
Brake disks 6,6 of the disk brakes 1, 1 are rotatably mounted along with a wheel disk7 by means of a front axle 5 supported on afrontfork4, and calipers 9,9 provided with pads 8,8 for engaging the brake disks 6 from opposite sides thereof in the usual way are supported on the front fork 4 on the opposite sides of the front wheel WAn oil passage loins connected to both of the calipers 9,9.
An oil passage 13 is connected to an output port 12 of the master cylinder 2, which generates hydraulic pressure in response to the operation of a brake lever 11, and the modulator3 is interposed between the oil passage 13 and the oil passage 10.
Amain bodyl4ofthemodulator3isofa cylindrical configuration whose diameter reduces step-wise towards the foremost end thereof. A cover 15 is connected to the rear end ofthe body 14 by means of bolt 16 and nut 17.
Nearto the foremost end of the body 14 an output hydraulic pressure chamber 18 is provided which communicates respectively with the oil passage 10 connected to the disk brakes 1,1, and an opening and closing valve 19 which is arranged to effect communication and interruption as between the oil passage 13 and the output hydraulic pressure chamber 18.
Specifically, a first connecting hole 21 having a step 20 facing the foremost end of the body 14 is axially bored in body 14, and a second connecting hole 23 having a step 22 is bored in the sidewall of the body 14 so as to connectgenerally in L-fashion with the inner end of the first connecting hole 21. The first connecting hole 21 receives therein a valve housing 24 abutting the step 20, and a connecting member 25 connectible to the oil passage 13, seal members 26,27 being provided respectively between housing 24 and mem ber 25 and the body 14.The second connecting hole 23 is formed towards the outer end thereofwith internal threads 28 forthe connection of the oil passage 10, whereby a connecting pipe member 29, which is urged against the step 22 by means of a member (notshown) threadedly engaged with the threads 28, is fitted into the second connecting hole 23. The output hydraulic pressure chamber 18 is defined between the valve housing 24 and the connecting pipe member 29, at the intersection between the connecting holes 21 and 23.
The opening and closing valve 19 includes a valve chamber 30 defined within the valve housing 24and the connecting member 25, a valve hole 31 interconnecting the valve chamber 30 and the output hydraulic pressure chamber 18, a spherical valve member32 located in the valve chamber30 and capable of closing the end ofthevalve hole 31 where it opens into the valve chamber30, a valve spring 33 acting between the valve member 32 and the connecting mem ber 25 to urge the valve member 32 in a closing direction, and a valve stem 34 integral with the valve member 32 and extending movably through the valve hole 31.
The valve chamber 30 is always in communication with the oil passage 13, and the valve stem 34 is normally urged againsttheforce of the valve spring 33 whereby the valve member 32 is moved in the opening direction and the valve chamber 30 is thus brought into communication with the output hydraulic pressure chamber 18.
The body 14 is formed with first, second, third and fourth coaxial bores 35,36,37 and 38, designates in that orderfrom the rear end thereof, which bores reduce step-wise in diameter and are all coaxial with the first connecting hole 21. Acylindrical sleeve portion 39 integral with the cover 15 is fitted into the first bore 35 and sealed by a seal member40, and an operating chamber 41 is defined between the body 14 and the cover 15.A projection 43 extending towards the operating chamber 41 is integrally provided on a partitioning wali 42 between the fourth bore 38 and the output hydraulic pressure chamber 18, and the partitioning wall 42 and projection 43 are bored to form a guide hole 44 which is coaxial with the valve hole 31 and extends between the output hydraulic pressure chamber 18 and the operating chamber 41.
A short cylindrical operating member 45 is slidably mounted in the guide hole 44 by way of a seal member 46, said operating member 45 being coaxially bored with a blind hole 47 which opens towards the opening and closing valve 19. The end region of the operating member 45 facing the valve 19 is notched on the side facing the second connecting hole 23. The outer diameter ofthe operating member45 is such astoform agap between it and the adjacent inner peripheral wall surface ofthe output hydraulic pressure chamber 18.
The free end of the valve stem 34 ofthe opening and closing valve 19 is slidably inserted into the blind hole 47 ofthe operating member 45, and accordingly the opening and closing valve 19 is opened and closed in response to movement ofthe operating member 45.
A rotational motor 49, for example a DC motor, is mounted on the cover 15 by means of a bolt48,and is actuated bya signal from a controller 50 such asa micro-computer. When the controller 50 judges from a signal inputfrom a sensor 51 mounted on thefront fork4thatthe front 'aheel W is about to lock, the controller outputs a signal for actuating the DC motor49.
An output shaft 52 ofthe DC motor 49 is connected to the operating member 45 through a transmission mechanism 53 received and arranged in the operating chamber 41, through which mechanism the rotational motion ofthe DCmotor49 is converted into linear motion of the operating member45.
Specifically, the transmission mechanism 53 includes a transmission member 54 which contacts the operating member 45, a bal I th read 55 interconnecting the output shaft 52 and the transmission member 54, and a spring 56forurging the transmission member 54to contact the operating member 45.
The transmission member 54 is ofcylindrical configuration with an outside diameter smallerthan thatofthefourth hole 38, and the projection 43 fits into the transmission member 54. A defining plate 57, which contacts the end ofthe projection 43 to definethe limit of movement ofthe transmission member 54, forms an integral central web portion of the transmission member. Acylindrical abutment member 58 projecting centrally from the defining plate 57 extends into the guide hole 44to contactthe operating member45.
Acylindrical guide member 61 is held inthethird bore 37 between a step 59 at the rear end of the fourth bore 38 and a stop ring 60 set in the surface of the third bore 37, and the transmission member 54 is slidably mounted inthe guide member61. A directly-driven bearing 63 having a plurality of axially arranged balls 62 is provided on the inner surface ofthe guide member 61, and a groove 64 which receives the balls 62 therein is formed axially on the outer surface of the transmission member 54, whereby the member 54 is precluded from axial rotation but is allowed to move axially.
The aforementioned ball thread 55 comprises a nut 65 secured to the transmission member 54 and a screw shaft 67 threadedly engaged with the nut 65 through a plurality of circulating balls 66, the screw shaft 67 being secured coaxiallytothe output shaft 52 of the DC motor 49. Accordingly, the nut 65 and thetransmission member 54 move axially in response to the rotation of the screw shaft 67, the spiral direction of the screw shaft 67 being set so that the member 54 is moved away from the opening and closing valve 19 when the DC motor 49 is actuated in response to the aforementioned signal from the controller 50, i.e. when the wheel is about to lock.
The screw shaft 67 is rotatably supported on the cover 15through a bearing 68, and seal member 69 is interposed between the screw shaft and the cover between the DC motor 49 and the bearing 68.
The spring 56 engages between the nut 65 and the cover 15, whereby the nut 65 and the transmission member 54 are urged towardsthe opening and closing valve 19 by the force of the spring 56.
Acommunicating hole 70 is bored in the side ofthe body 14to communicate with the operating chamber 41, and an oil passage 71 connects the communicating hole 70 to a reservoir72 of the master cylinder 2. Accordingly, working oil is supplied to the operating chamber to serve as lubricating oil for the transmission mechanism 53.
The operation of the above-described apparatus will now be described.
In the normal operating condition the valve 19 is open and the oil passage 13 isthus in communication with the output hydraulic pressure chamber 18. Therefore, when the brake lever 11 is operated, hydraulic pressure output from the output port 12 of the master cylinder 2 act on both ofthe disk brakes 1, 1 to provide a braking force.
When, at the time of such braking, circumstances arise in which the front wheel W is about to lock, a signal is inputfrom the controller 50 to the DC motor 49, in response to the signal from the sensor 51, whereby the DC motor 49 is actuated.
The rotational actuation of the DC motor 49 is converted into linear motion of the transmission member 54 by the transmission mechanism 53, and the member 54 is thereby moved in the direction away from the valve 19. As a result, the operating member 45 is moved toward the transmission member 54 bytheforce of the valve spring 33, and the valve hole 31 is closed by the spherical valve member 32 to interrupt communication between the oil passage 13 and the output hydraulic pressure chamber 18. Furthermore, the volume of the output hydraulic pressure chamber 18 increases with the movement ofthe operating member45towards and into the guide hole 44 in response to the movement of the abutment member 58.Thus, the braking hydraulic pressure acting on the disk brakes 1,1 is reduced, thus preventing the front wheel Wfrom locking.
When the front wheel W recovers its rotation, the rotation of the DC motor 49 stops, but the nut 65 and the transmission member 54 are moved towards the opening and closing valve l9bytheforceofthe spring 56, thereby causing reverse rotation of the screw shaft 67 and the output shaft 52. Thus the operating member 45 is now moved in the direction to reduce the volume of the output hydraulic pressure chamber 18, so as to increase the braking hydraulic pressure. Then, if the wheel is again about to lock, the DC motor is again actuated. This cycle of operation is repeatedly carried outto preventthe front wheel Wfrom the locking.If desired, to increase the responsiveness of the system, when the front wheel W recovers its rotation the DC motor 49 may be reversely rotated.
When, eventually, movement ofthe operating member45to reduce the volume of the output hydraulic pressure chamber 18 does not cause the front wheel Wto sta rtto lock, the transmission member 54 moves further towards the valve 19 and the valve stem 34 once again comes into contact with the bottom of the hole 47, whereby the valve stem 34 and the valve member 32 are raised to open the valve 19 and braking hydraulic pressure mayonce again be supplied from the master cylinder 2 to the disk brakes 1,1.
In the antilock braking system as described above, as the DC motor 49 is mounted on the modulator3 and the operating member 45 is driven by the DC motor 49, the responsiveness ofthe system can be improved. Furthermore, since the opening and closing strokes of the valve 19 can be freely set by selection ofthe spiral form of the screw shaft 67, the
DC motor 49 can be separate from the actuator system formed by the opening and closing valve 19 and the transmission mechanism 53, whereby those parts of the actuator system requiring high precision in seals, assembly, strokes and the like may be constituted separately from low precision parts of the system.
In addition,the hydraulic pressure system is made moresimple in construction and accordinglythe number of parts can be reduced, and weight reduction and miniaturization can be facilitated.
Other types of motor such as an AC motor or a step motor may be used in place of a DC motor, thus providing great freedom in the selection of a motor.
It isto be clearly understood that there are no particularfeatures of the foregoing specification, or of any claims appended hereto, which are at present regarded as being essential to the performance of the present invention, and that any one or more of such features or combinations thereof may therefore be included in, added to, omitted from or deleted from any of such claims if and when amended during the prosecution ofthis application or in the filing or prosecution of any divisional application based thereon.
Claims (7)
1. An antilockbraking system including a modulator operatively interposed between a master cylinder and a brake associated with a wheel,the said modulator including an output hydraulic pressure chamber connected to the brake, a valve operative to open and close communication between the said master cylinder and the said output hydraulic pressure chamber, an operating member for the said valve, movement of the said operative member in a valve closing direction being arranged to cause an increase in the volume of the said output hydraulic pressure chamber, a rotational motor mounted to the said modulator for driving the said operating member, means for operating the motor in response to a state in which the wheel is aboutto lock, and transmission means between the motor and the operating member arranged to convert rotational motion of the motor into linear motion of the operating member.
2. An antilock braking system as claimed in claim 1, wherein the said transmission means includes a screw and a nut of which one is connected to the said motor and the other is arranged to act on the said operating member.
3. An antilock braking system as claimed in claim 2, wherein the said screw is connected to the motor.
4. An antilock braking system as claimed in any preceding claim, including spring means arranged to urge the said operating member in the valve opening direction.
5. An antilock braking system as claimed in claims 3 and 4, wherein the said spring means acts directly on the said nut, and the said screw and nut are interconnected by a ball thread.
6. An antilock braking system as claimed in any preceding claim, including means for operating the said motor in the reverse direction in response to termination of the state in which the wheel is about to lock.
7. An antilock braking system as claimed in claim 1, substantially as herein before described with reference to the accompanying drawing.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61054445A JPH0657525B2 (en) | 1986-03-12 | 1986-03-12 | Anti-lock break device |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| GB8705039D0 GB8705039D0 (en) | 1987-04-08 |
| GB2188111A true GB2188111A (en) | 1987-09-23 |
| GB2188111B GB2188111B (en) | 1989-11-15 |
Family
ID=12970900
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB8705039A Expired GB2188111B (en) | 1986-03-12 | 1987-03-04 | Antilock braking system |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPH0657525B2 (en) |
| DE (1) | DE3707666A1 (en) |
| GB (1) | GB2188111B (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2202018A (en) * | 1987-03-09 | 1988-09-14 | Brembo Spa | Vehicle antiskid valve |
| EP0297797A1 (en) * | 1987-06-27 | 1989-01-04 | LUCAS INDUSTRIES public limited company | An hydraulic anti-skid vehicle braking system |
| EP0317183A2 (en) * | 1987-11-20 | 1989-05-24 | LUCAS INDUSTRIES public limited company | Modulator assembly |
| EP0317304A2 (en) * | 1987-11-20 | 1989-05-24 | LUCAS INDUSTRIES public limited company | Wheel skid correction device for vehicle braking system |
| DE3803079A1 (en) * | 1988-02-03 | 1989-08-17 | Bosch Gmbh Robert | Electromechanically operated pressure modulator for antilock and traction control systems |
| US5000523A (en) * | 1989-05-17 | 1991-03-19 | General Motors Corporation | Anti-lock braking system with electromagnetic brake |
| US5112116A (en) * | 1989-05-17 | 1992-05-12 | General Motors Corporation | Anti-lock braking system with electromagnetic brake |
| US5184877A (en) * | 1990-10-09 | 1993-02-09 | Honda Giken Kogyo Kabushiki Kaisha | Hydraulic braking pressure control device |
| US5433514A (en) * | 1993-03-16 | 1995-07-18 | Nissan Motor Co., Ltd. | Pressure control actuator for a brake control system |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4038033A1 (en) * | 1990-11-29 | 1992-06-04 | Teves Gmbh Alfred | Vehicular antilock hydraulic braking system with isolating valve - has low and high pressure reservoirs with isolating piston recessed into piston of high pressure reservoir |
| AU4069497A (en) * | 1996-08-13 | 1998-03-06 | Kelsey-Hayes Company | Dual action ball screw pump |
| US6079797A (en) * | 1996-08-16 | 2000-06-27 | Kelsey-Hayes Company | Dual action ball screw pump |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2057613A (en) * | 1979-08-14 | 1981-04-01 | Lucas Industries Ltd | Improvements in hydraulic anti-skid braking systems for vehicles |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3420580A (en) * | 1967-05-11 | 1969-01-07 | Trw Inc | Skid control device |
| DE1916662A1 (en) * | 1969-04-01 | 1970-10-08 | Baezold Karl | Adjusting device for brake slip regulator |
| JPS5821053A (en) * | 1981-07-25 | 1983-02-07 | Keiichi Tachikawa | Linear motion device |
| JPS60103773U (en) * | 1983-12-22 | 1985-07-15 | アイダエンジニアリング株式会社 | flow control valve |
| US4756391A (en) * | 1987-07-06 | 1988-07-12 | General Motors Corporation | Brake system actuator with a return spring |
-
1986
- 1986-03-12 JP JP61054445A patent/JPH0657525B2/en not_active Expired - Lifetime
-
1987
- 1987-03-04 GB GB8705039A patent/GB2188111B/en not_active Expired
- 1987-03-10 DE DE19873707666 patent/DE3707666A1/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2057613A (en) * | 1979-08-14 | 1981-04-01 | Lucas Industries Ltd | Improvements in hydraulic anti-skid braking systems for vehicles |
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4886323A (en) * | 1987-03-09 | 1989-12-12 | Brembo S.P.A. | Antiskid device useful in a brake system of a motorvehicle |
| GB2202018B (en) * | 1987-03-09 | 1991-04-24 | Brembo Spa | Antiskid device |
| GB2202018A (en) * | 1987-03-09 | 1988-09-14 | Brembo Spa | Vehicle antiskid valve |
| EP0297797A1 (en) * | 1987-06-27 | 1989-01-04 | LUCAS INDUSTRIES public limited company | An hydraulic anti-skid vehicle braking system |
| US4957331A (en) * | 1987-06-27 | 1990-09-18 | Lucas Industries Public Limited Company | Hydraulic anti-skid vehicle braking system |
| EP0317183A3 (en) * | 1987-11-20 | 1990-07-11 | Lucas Industries Public Limited Company | Modulator assembly |
| US4909577A (en) * | 1987-11-20 | 1990-03-20 | Lucas Industries Public Limited Company | Wheel skid correction device for vehicle braking system |
| US4922121A (en) * | 1987-11-20 | 1990-05-01 | Lucas Industries Public Limited Company | Modulator assembly |
| EP0317304A2 (en) * | 1987-11-20 | 1989-05-24 | LUCAS INDUSTRIES public limited company | Wheel skid correction device for vehicle braking system |
| EP0317304A3 (en) * | 1987-11-20 | 1990-11-22 | Lucas Industries Public Limited Company | Wheel skid correction device for vehicle braking system |
| EP0317183A2 (en) * | 1987-11-20 | 1989-05-24 | LUCAS INDUSTRIES public limited company | Modulator assembly |
| DE3803079A1 (en) * | 1988-02-03 | 1989-08-17 | Bosch Gmbh Robert | Electromechanically operated pressure modulator for antilock and traction control systems |
| US5000523A (en) * | 1989-05-17 | 1991-03-19 | General Motors Corporation | Anti-lock braking system with electromagnetic brake |
| US5112116A (en) * | 1989-05-17 | 1992-05-12 | General Motors Corporation | Anti-lock braking system with electromagnetic brake |
| US5184877A (en) * | 1990-10-09 | 1993-02-09 | Honda Giken Kogyo Kabushiki Kaisha | Hydraulic braking pressure control device |
| US5433514A (en) * | 1993-03-16 | 1995-07-18 | Nissan Motor Co., Ltd. | Pressure control actuator for a brake control system |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0657525B2 (en) | 1994-08-03 |
| DE3707666C2 (en) | 1991-10-02 |
| JPS62214042A (en) | 1987-09-19 |
| GB8705039D0 (en) | 1987-04-08 |
| GB2188111B (en) | 1989-11-15 |
| DE3707666A1 (en) | 1987-09-24 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PCNP | Patent ceased through non-payment of renewal fee |
Effective date: 19990304 |