EP0293209B1 - Ventilsteuervorrichtung in einer Brennkraftmaschine - Google Patents

Ventilsteuervorrichtung in einer Brennkraftmaschine Download PDF

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Publication number
EP0293209B1
EP0293209B1 EP19880304802 EP88304802A EP0293209B1 EP 0293209 B1 EP0293209 B1 EP 0293209B1 EP 19880304802 EP19880304802 EP 19880304802 EP 88304802 A EP88304802 A EP 88304802A EP 0293209 B1 EP0293209 B1 EP 0293209B1
Authority
EP
European Patent Office
Prior art keywords
rocker
rocker arms
proximity sensor
piston means
piston
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.)
Expired
Application number
EP19880304802
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English (en)
French (fr)
Other versions
EP0293209A1 (de
Inventor
Kunno Tsuneo
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Honda Motor Co Ltd
Original Assignee
Honda Motor Co Ltd
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
Priority claimed from JP62127178A external-priority patent/JPS63147909A/ja
Application filed by Honda Motor Co Ltd filed Critical Honda Motor Co Ltd
Publication of EP0293209A1 publication Critical patent/EP0293209A1/de
Application granted granted Critical
Publication of EP0293209B1 publication Critical patent/EP0293209B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F2001/244—Arrangement of valve stems in cylinder heads
    • F02F2001/247—Arrangement of valve stems in cylinder heads the valve stems being orientated in parallel with the cylinder axis

Definitions

  • the present invention relates to a valve operating apparatus in an internal combustion engine. More particularly, the invention involves valve operating apparatus including a sensing device for monitoring the operational condition of the apparatus.
  • valve operating apparatus is effective, during periods of low-speed operation of the engine, to reduce the number of operative valves and, during periods of high speed operation of the engine, to not only effect the operation of all of the valves, but to vary their timing in accordance with engine operating conditions as well.
  • One such arrangement is disclosed in Japanese Laid-Open Patent Publication No. 61-19911.
  • Such arrangement includes a camshaft rotatable in synchronism with the rotation of an engine.
  • the camshaft has an integral low-speed cam aligned with one of the intake or exhaust valves, which cam has a cam profile corresponding to low-speed operation of the engine.
  • a rocker shaft carries a first rocker arm angularly movably supported on the rocker shaft and being in sliding contact with the low-speed cam and engageable with said one intake or exhaust valve.
  • a second rocker cam is also angularly movably supported on the rocker shaft and engageable with the other intake or exhaust valve, while a third rocker arm is held in sliding contact with the high-speed cam.
  • the first, second and third rocker arms are relatively angularly displaceable in mutual sliding contact, and have coupling means for selectively disconnecting or interconnecting the rocker arms to allow them to either be relatively angularly displaceable or to be angularly displaced in unison.
  • the coupling device includes pistons slidably fitted in mutually communicating guide holes defined in the rocker arms, the pistons being hydraulically operable to interconnect the rocker arms.
  • EP-A-0213759 on which the precharacterising part of claim 1 is based. It is proposed in EP-A-0265281 (falling under Article 54(3)) to detect the position of the pistons with an electromagnetic detector or an electric contact arrangement.
  • apparatus for operating intake or exhaust valves in an internal combustion engine including a plurality of rocker arms for opening and closing said valves; cam means for driving said rocker arms to impart a mode of operation to said valves; mutually registrable guide holes in said rocker arms; piston means carried by said rocker arms in said guide holes; and a rocker shaft pivotally mounting said rocker arms and having a hollow interior connecting with a source of operating fluid to operate said piston means, whereby said piston means is selectively movable between adjacent guide holes for connecting or disconnecting said rocker arms to vary the mode of operation of said valves; characterised by sensing means for determining the positional condition of said piston means, such sensing means comprising an electrically operated proximity sensor whose output signal is varied in response to positional changes in said piston means; and partition means in said rocker shaft dividing the interior thereof into a pair of distinct, parallel passages, one of said passages connecting with said source of operating fluid for operating said piston means and the other of said passages housing an electric wire to said sensor.
  • an internal combustion engine body (not shown) has a pair of intake valves 1a, 1b which can be opened and closed by the coaction of a pair of low-speed cams 3a, 3b and a single high-speed cam 4.
  • the cams 3a, 3b, 4 are generally of egg-shaped cross section and are integrally formed on a camshaft 2 that is synchronously rotatable at a speed ratio of 1/2 with respect to the speed of rotation of a crankshaft (not shown).
  • First enough third transmitting members in the form of rocker arm 5 through 7 are swingable in engagement with the cams 3a, 3b, 4.
  • the internal combustion engine also has a pair of exhaust valves (not shown) which are opened and closed in the same manner as the intake valves 1a, 1b.
  • the first through third rocker arms 5 through 7 are pivotally supported in mutually adjacent relation on a rocker shaft 8 fixed below the camshaft 2 and extending parallel thereto.
  • the first and third rocker arms 5, 7 are basically of the same shape, and have their base portions pivotally supported on the rocker shaft 8 and free ends extending above the intake valves 1a, 1b.
  • Tappet screws 9a, 9b are adjustably threaded through the free ends of the rocker arms 5, 7 and are held against the upper ends of the intake valves 1a, 1b.
  • the tappet screws 9a, 9b are locked against being loosened by means of lock nuts 10a, 10b, respectively.
  • the second rocker arm 6 is pivotally supported on the rocker shaft 8 between the first and third rocker arms 5, 7.
  • the second rocker arm 6 extends slightly from the rocker shaft 8 toward an intermediate position between the intake valves 1a, 1b.
  • the second rocker arm 6 has a cam slipper 6a on its upper surface which is held in sliding contact with the high-speed cam 4.
  • a lifter 12 slidably fitted in a guide hole 11a defined in a cylinder head 11 has an upper end held against the lower surface of the end of the second rocker arm 6.
  • the lifter 12 is normally urged upwardly by a coil spring 13 disposed under compression between the inner surface of the lifter 12 and the bottom of the guide hole 11a for keeping the cam slipper 6a of the second rocker arm 6 in sliding contact with the high-speed cam 4 at all times.
  • the camshaft 2 is rotatably supported above the engine body, as described above.
  • the low-speed cams 3a, 3b are integrally formed on the camshaft 2 in alignment with the first and third rocker arms 5, 7 and the high-speed cam 4 is integrally formed on the camshaft 2 in alignment with the second rocker arm 6.
  • the low-speed cams 3a, 3b have a relatively small lift and a cam profile suitable for low-speed operation of the engine.
  • the low-speed cams 3a, 3b have outer peripheral surfaces held in sliding contact with the respective cam slippers 5a, 7a on the upper surface of the first and third rocker arms 5, 7.
  • the high-speed cam 4 is of a cam profile suitable for high-speed operation of the engine and has a larger lift and a wider angular extent than the low-speed cam 3a, 3b.
  • the high-speed cam 4 has an outer peripheral surface held in sliding contact with the cam slipper 6a of the second rocker arm 6, as described above.
  • the lifter 12 is omitted from illustration in Figure 3.
  • first through third rocker arms 5 through 7 is switchable between a condition in which they can swing together and a condition in which they are relatively angularly displaceable by a coupling device 14 (described hereafter) that includes pistons mounted for movement in guide holes defined centrally through the rocker arms 5 through 7 parallel to the rocker shaft 8.
  • a coupling device 14 that includes pistons mounted for movement in guide holes defined centrally through the rocker arms 5 through 7 parallel to the rocker shaft 8.
  • Retainers 15a, 15b are disposed on the upper portions of the intake valves 1a, 1b, respectively.
  • Valve springs 16a, 16b are interposed between the retainers 15a, 15b and the engine body and disposed around the stems of the intake valves 1a, 1b for normally urging the valves 1a, 1b in a closing direction, i.e., upwardly as viewed in Figure 3.
  • the first rocker arm 5 has a first guide hole 17 opening toward the second rocker arm 6 and extending parallel to the rocker shaft 8.
  • the first rocker arm 5 also has a smaller-diameter hole 18 near the closed end of the first guide hole 17, with a step 19 being defined between the smaller-diameter hole 18 and the first guide hole 17.
  • the second rocker arm 6 has a second guide hole 20 communicating with the first guide hole 17 in the first rocker arm 5.
  • the second guide hole 20 extends between the opposite sides of the second rocker arm 6.
  • the third rocker arm 7 has a third guide hole 21 communicating with the second guide hole 20.
  • the third rocker arm 7 also has a step 22 and a smaller-diameter hole 23 adjacent the closed end of the third guide hole 21.
  • a smaller-diameter through-hole 24 extends through the closed end of the third guide hole 21 in the third rocker arm 7 concentrically therewith.
  • the first through third guide holes 17, 20, 21 accommodate therein, a first piston 25 movable between a position in which the first and second rocker arms 5, 6 are interconnected and a position in which they are disconnected; a second piston 26 movable between a position in which the second and third rocker arms 6, 7 are interconnected and a position in which they are disconnected; a stopper 27 for limiting movement of the pistons 25, 26; and a coil spring 28 for urging the stopper 27 and the pistons 25, 26 toward the disconnecting positions.
  • the first piston 25 is slidable in the first and second guide holes 17, 20, and defines a hydraulic pressure chamber 29 between the end of the first guide hole 17 and the end face of the first piston 25.
  • the rocker shaft 8 has a pair of hydraulic passages 30, 31 defined therein that communicate with a hydraulic pressure supply device (not shown).
  • a hydraulic pressure supply device not shown.
  • the axial dimension of the first piston 25 is selected such that when one end thereof abuts against the step 19 in the first guide hole 17, the other end does not project from the side surface of the first rocker arm 5 which faces the second rocker arm 6.
  • the axial dimension of the second piston 26 is equal to the overall length of the second guide hole 20 and is slidable in the second and third guide holes 20, 21.
  • the stopper 27 has on one end thereof a circular plate 27a slidably fitted in the third guide hole 21. It also has on the other end thereof a guide rod 27b extending through the smaller-diameter hole 24 in the third rocker arm 7.
  • the coil spring 28 is disposed around the guide rod 27b between the circular plate 27a of the stopper 27 and the bottom of the smaller-diameter hole 23.
  • the guide rod 27b has a plurality of axial grooves 27c defined in the outer peripheral surface thereof adjacent its distal end.
  • the third rocker arm 7 has a hydraulic passage 34.
  • the rocker shaft 8 has a hole 35 defined in a peripheral wall thereof surrounded by the third rocker arm 7.
  • the fluid passage 31 communicates with the third guide hole 21 through the hydraulic passage 34 and the hole 35 irrespective of how the third rocker arm 7 is angularly moved.
  • the hydraulic passage 34 of the third rocker arm 7 is disposed in such a position that it is caused to communicate with the third guide hole 21 when the second piston 26 and the stopper 27 are in their respective positions in which the rocker arms are disconnected (as shown in Figure 4) but will not communicate with the third guide hole 21 when the second piston 26 and the stopper 27 are in their respective positions in which the rocker arms are interconnected (as shown in Figure 5).
  • Lubricating oil supplied under a prescribed pressure from a lubricating oil pump 40 operated by the crankshaft of the engine is divided into two flows, one supplied via a solenoid-operated valve 41 to the working oil supply passage 30 in the rocker shaft 8 and the other supplied via an orifice 42 into the fluid passge 31.
  • the passages 30, 31 and the outlet of the pump 40 are each connected to individual hydraulic pressure detectors 43 through 45 which monitor the hydraulic pressures at all times.
  • the first and third rocker arms 5, 7 are angularly moved in sliding contact with the low-speed cams 3a, 3b in response to rotation of the camshaft 2, and the opening timing of the intake valves 1a, 1b is delayed and the closing timing thereof is advanced, with the lift thereof being reduced.
  • the second rocker arm 6 is angularly moved in sliding contact with the high-speed cam 4, but such angular movement does not affect operation of the intake valves 1a, 1b in any way.
  • the fluid passage 31 is supplied with oil under pressure at all times to lubricate the sliding surface of the rocker shaft 8 and the rocker arms 5 through 7 through oil holes (not shown). Such oil is discharged into the engine through the oil hole 35 on the rocker shaft 8, the oil hole 34 of the third rocker arm 7, and the axial grooves 27c of the guide rod 27b. Under this condition, the hydraulic pressure detector 44 on the working oil supply passage 30 indicates a pressure P2 of 0, and the hydraulic pressure detector 45 indicates a highest source pressure P3.
  • the solenoid-operated valve 41 When the engine is to operate in a high-speed range, the solenoid-operated valve 41 is opened to supply working oil pressure to the hydraulic pressure chamber 29 of the coupling device 14 through the working oil supply passage 30, the hole 33 of the rocker shaft 8, and the oil hole 32. As shown in Figure 5, the first piston 25 is moved under the influence of the pressure of the oil into the guide hole 20 in the second rocker arm 6 against the bias of the coil spring 28, pushing the second piston 26 into the guide hole 21 in the third rocker arm 7.
  • first and second pistons 25, 26 are moved together axially until the circular plate 27a of the stopper 27 engages the step 22, whereupon the first and second rocker arms 5, 6 are interconnected by the first piston 25 and the second and third rocker arms 6, 7 are interconnected by the second piston 26.
  • the first and third rocker arms 5, 7 are angularly moved with the second rocker arm 6 since the extent of swinging movement of the second rocker arm 6 in sliding contact with the high-speed cam 4 is largest. Accordingly, the opening timing of the intake valves 1a, 1b is advanced and the closing timing thereof is delayed and the lift thereof is increased according to the cam profile of the high-speed cam 4.
  • the operation condition of the pistons 25, 26 can therefore be confirmed by a change in the pressure P1 in the fluid passage 31 or a change in the pressure difference between the pressure P1 in the fluid passage 31 and the pressure P2 in the working oil supply passage 30 or between the pressure P1 in the fluid passage 31 and the source pressure P3. Failure of operation of the pistons due to malfunctioning of the solenoid-operated valve 41 can be detected by monitoring the pressure P2 in the working oil supply passage 30.
  • Figure 8 shows another embodiment of fluid circuit in which pneumatic pressure is suppied to the fluid passage 31 and the difference between pressures P4, P5 downstream and upstream of an orifice 42 is monitored.
  • the pistons may be driven, not only by the described hydraulic arrangement, but also by an electrical or mechanical device.
  • the rocker arms may be centrally pivoted, rather than pivoted at their ends.
  • the transmitting members may be direct-type bucket lifters.
  • the device may be structurally modified such that the fluid passage may be vented to the exterior when the rocker arms are interconnected.
  • the position of the pistons may be detected by an electromagnetic detector, or an electric arrangement in which a contact is attached to the guide rod 27b of the stopper 27 so that the projection of the guide rod 27b out of the hole 24 of the second rocker arm 7 can be electrically detected by the attached contact.
  • an electromagnetic detector or an electric arrangement in which a contact is attached to the guide rod 27b of the stopper 27 so that the projection of the guide rod 27b out of the hole 24 of the second rocker arm 7 can be electrically detected by the attached contact.
  • FIG 9 shows a first embodiment of the present invention in which parts that correspond to those in the previous Figures are denoted by identical reference numerals and will not be described in detail.
  • the hydraulic passage 31 in the previous Figures is used as a hollow passage 46 for the passage of a lead wire 47a, which is hereinafter described.
  • An electromagnetic proximity sensor 47 of a known type comprising a coil and a magnet core is pressed into an outer peripheral wall of the rocker shaft 8 near the wire passage 46.
  • the lead wire 47a of the proximity sensor 47 extends through the wire passage 46 and is connected to a control unit (not shown).
  • the proximity sensor 47 has its detecting end directed radially outwardly of the rocker shaft and accommodated in a housing hole 48 formed in the second rocker arm 6.
  • the housing hole 48 is arranged such that the second rocker arm 6 will not physically interfere with the proximity sensor 47 throughout the entire range of angular movement of the second rocker arm 6.
  • the second piston 26 has an annular recess 49 formed about its outer peripheral surface near the tip end of the proximity sensor 47.
  • the recess 49 and the tip end of the proximity sensor 47 are aligned with each other when the coupling device 14 is in the rocker arm connecting position as shown in Figure 9.
  • the proximity sensor 47 generates an "OFF" signal when the coupling device 14 is in the rocker arm connecting position.
  • the outer peripheral surface of the second piston 26 confronts the tip end of the proximity sensor 47, which is then triggered to generate an "ON" signal.
  • the signal from the proximity sensor 47 is varied dependent on movement of the second piston 26 to detect how the coupling device 14 is operated.
  • Figure 10 illustrates a second embodiment of the present invention in which parts corresponding to those of the previous Figures are designated by identical reference numerals and will not be described in detail.
  • the proximity sensor 47 which is substantially identical to that of the proximity sensor of the first embodiment, is mounted on a rocker shaft holder 50. As the tip end of the guide rod 27b of the stopper 27 is moved toward or away from the proximity sensor 47, the signal produced by the proximity sensor 47 is varied to detect how the coupling device 14 is operated.
  • each of the first and second embodiments may be replaced with a limit switch having mechanical contacts.
  • the operation timing of the two valves combined with the three rocker arms is changed in the above embodiments.
  • the present invention is equally applicable to a valve operation timing changing device for disabling one of the valves combined with two rocker arms at a certain engine rotational speed.
  • the present invention provides a device for changing the valve operation timing of an internal combustion engine, the device being capable of reliably detecting the operating condition of the pistons of the coupling means with a relatively simple structure so that corrective measures can be taken rapidly if the pistons fail to operate normally.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (6)

1. Vorrichtung zur Betätigung von Einlaß- oder Auslaßventilen (1a, 1b) in einer Brennkraftmaschine, umfassend eine Mehrzahl Kipphebel (5, 6, 7) zum Öffnen und Schließen der Ventile, Nockenmittel (3a, 3b, 4) zum Antrieb der Kipphebel, um den Ventilen einen Betriebsmodus zu verleihen, wechselweise in Registerstellung bringbare Führungslöcher (17, 20, 21) in den Kipphebeln, ein durch die Kipphebel in den Führungslöchern gehaltenes Kolbenmittel (25, 26) und eine Kipphebelwelle (8), die die Kipphebel schwenkbeweglich hält und die ein hohles Inneres hat, das mit einer Betätigungsfluidquelle zur Betätigung des Kolbenmittels in Verbindung steht, wodurch das Kolbenmittel zwischen benachbarten Führungslöchern zum Verbinden oder Trennen der Kipphebel selektiv beweglich ist, um den Betätigungsmodus der Ventile zu ändern, gekennzeichnet durch Erfassungsmittel zur Bestimmung des Positionszustands des Kolbenmittels, wobei diese Erfassungsmittel einen elektrisch betriebenen Näherungssensor (47) aufweisen, dessen Ausgangssignal in Antwort auf Positionsveränderungen in dem Kolbenmittel geändert wird und Teilungsmittel in der Kipphebelwelle, die deren Inneres in ein Paar verschiedene parallele Passagen (30, 46) unterteilt, wobei eine der Passagen (30) mit der Betätigungsfluidquelle zur Betätigung des Kolbenmittels in Verbindung steht und die andere der Passagen (46) eine elektrische Leitung (47a) zu dem Sensor aufnimmt.
2. Vorrichtung nach Anspruch 1, wobei der Näherungssensor (47) elektromagnetisch betätigt wird.
3. Vorrichtung nach Anspruch 1, wobei der Näherungssensor ein elektrisch betätigter Schalter mit mechanisch betätigten Kontakten ist.
4. Vorrichtung nach Anspruch 1, 2 oder 3, umfassend Mittel in der Wand der Kipphebelwelle (8) zur festen Anbringung des Näherungssensors (47) und Mittel (48), die eine Öffnung in dem Kipphebel (6) nahe dem Sensor bilden und mit dem Führungsloch (20) darin in Verbindung stehen, um das Kolbenmittel (25, 26) dem Sensor zu exponieren.
5. Vorrichtung nach Anspruch 1, 2 oder 3, umfassend einen die Kipphebelwelle (8) haltenden Kipphebelwellenhalter (50) und Mittel in dem Kipphebelwellenhalter zur Positionierung des Näherungssensors (47) in Erfassungsbeziehung zu dem Kolbenmittel (25, 26).
6. Vorrichtung nach Anspruch 5, wobei der Näherungssensor (47) in axialer Ausrichtung zu dem Kolbenmittel (25, 26) angeordnet ist.
EP19880304802 1987-05-26 1988-05-26 Ventilsteuervorrichtung in einer Brennkraftmaschine Expired EP0293209B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP62127178A JPS63147909A (ja) 1986-10-23 1987-05-26 内燃機関の弁作動特性可変制御装置
JP127178/87 1987-05-26

Publications (2)

Publication Number Publication Date
EP0293209A1 EP0293209A1 (de) 1988-11-30
EP0293209B1 true EP0293209B1 (de) 1991-11-27

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19880304802 Expired EP0293209B1 (de) 1987-05-26 1988-05-26 Ventilsteuervorrichtung in einer Brennkraftmaschine

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EP (1) EP0293209B1 (de)
DE (1) DE3866430D1 (de)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2577252B2 (ja) * 1988-10-11 1997-01-29 本田技研工業株式会社 内燃機関の動弁装置
GB9003603D0 (en) * 1990-02-16 1990-04-11 Lotus Group Plc Cam mechanisms
US5253621A (en) * 1992-08-14 1993-10-19 Group Lotus Plc Valve control means
EP0620360A3 (de) * 1990-02-16 1995-01-18 Lotus Group Ltd Ventilstösselanordnung.
DE4235796C2 (de) * 1992-10-23 1996-07-11 Daimler Benz Ag Verfahren zur Überwachung des Schaltvorgangs einer Koppelvorrichtung zur Betätigung von Gaswechselventilen
US5406835A (en) * 1992-06-27 1995-04-18 Mercedes Benz Ag Method for monitoring the switching process of a coupling device
DE59400590D1 (de) * 1993-11-08 1996-10-10 Daimler Benz Ag Vorrichtung zum Betreiben von Ventilen einer Brennkraftmaschine
DE102008027649A1 (de) * 2008-06-10 2009-12-17 Man Diesel Se Ventilbetrieb für eine Brennkraftmaschine

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62121811A (ja) * 1985-07-31 1987-06-03 Honda Motor Co Ltd 内燃機関の動弁装置
JPS63147909A (ja) * 1986-10-23 1988-06-20 Honda Motor Co Ltd 内燃機関の弁作動特性可変制御装置

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Publication number Publication date
EP0293209A1 (de) 1988-11-30
DE3866430D1 (de) 1992-01-09

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