EP0318534A1 - Pompe d'injection a distributeur du type a pistons radiaux. - Google Patents

Pompe d'injection a distributeur du type a pistons radiaux.

Info

Publication number
EP0318534A1
EP0318534A1 EP88904479A EP88904479A EP0318534A1 EP 0318534 A1 EP0318534 A1 EP 0318534A1 EP 88904479 A EP88904479 A EP 88904479A EP 88904479 A EP88904479 A EP 88904479A EP 0318534 A1 EP0318534 A1 EP 0318534A1
Authority
EP
European Patent Office
Prior art keywords
pump
distributor
piston
interior
switching valve
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
Application number
EP88904479A
Other languages
German (de)
English (en)
Other versions
EP0318534B1 (fr
Inventor
Andre Brunel
Jean Paul Morel-Fourrier
Jean Leblanc
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0318534A1 publication Critical patent/EP0318534A1/fr
Application granted granted Critical
Publication of EP0318534B1 publication Critical patent/EP0318534B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/02—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements
    • F02M41/06—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements the distributor rotating
    • F02M41/063—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements the distributor rotating the distributor and rotary valve controlling fuel passages to pumping elements being combined
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/02—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements
    • F02M41/06—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements the distributor rotating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0205—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine
    • F02M63/0215—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine by draining or closing fuel conduits

Definitions

  • the invention is based on one
  • Fuel volume is determined depending on parameters of the internal combustion engine - such as load and speed, by the time of closing and opening of the electrical switching valve.
  • the switching valve closes, the fuel injection begins in the respective cylinder of the internal combustion engine, while when the switching valve is opened, the pump work chamber is connected to the relief chamber and the fuel injection is suddenly ended. If the switching valve in the Way that it gets stuck in its closed position and no longer opens, the engine is always independent of the load with the maximum
  • the distributor fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage that, in the event of the switching valve getting stuck in its closed position, the delivery of fuel from the pump workspace to the injection nozzle is interrupted.
  • the internal combustion engine comes to a standstill because of a missing ignition mixture.
  • the defect in the switching valve is detected by a monitoring device, which then issues a closing command to the second switching valve.
  • a criterion for the defect of the first switching valve can be, for example, the increase in the speed of the internal combustion engine beyond a maximum speed.
  • the second switching valve is expediently designed such that it is normally closed and opens when activated. The switching valve then closes when the control is omitted, so that the closing command consists in interrupting the excitation current for the electromagnet of the second switching valve. In this way, the fuel delivery is interrupted even when the control line of the second switching valve is disturbed.
  • the second switching valve can be much simpler and therefore cheaper than the first switching valve.
  • Fig. 1 each shows a longitudinal section of one to 4 distributor fuel injection pump of the radial piston type in four
  • the radial piston type distributor fuel injection pump shown in longitudinal section in FIG. 1 has a cup-shaped housing 10 and a cover 11 closing it, which is pushed in from the open end of the housing 10 and delimits a pump interior 12 with a bottom 10a integral with the housing 10.
  • the pump interior 12 is filled with fuel under low pressure and via a
  • a drive shaft 15 is passed through the bottom 10a of the housing 10 in a liquid-tight manner, which widens in a pot-shaped manner in the pump interior 12 and rotates with it along its edge connected cam ring 16 carries.
  • the cam ring 16 has on its inside in a known manner a cam track 17 with radially inwardly directed cams, the number and sequence of the number and sequence of radial pump pistons contained in the fuel injection pump and the number with these pump pistons per revolution of the drive shaft 15 piston strokes to be carried out are adapted.
  • a feed pump 18 sits on the drive shaft 15 and is connected to the fuel tank via an intake line 19 and to the pump interior 12 via a pressure line 20 and thereby ensures the fuel filling of the pump interior 12.
  • a distributor piston 21 is also connected to the drive shaft 15 in a rotationally fixed but axially displaceable manner, the axis of which is aligned with the axis of the drive shaft 15.
  • Distributor piston 21 is guided, except for the end connected to the drive shaft 15 in the pump interior 12, in a distributor cylinder 22 which is held in a bore 23 of the cover 11 which is coaxial with the axis of the drive shaft 15.
  • Guides 24 are provided in the cover 11 and in the distributor cylinder 22 adjacent to the cam track 17, radially inward thereafter, which are evenly distributed over the circumference of the distributor cylinder 22 and extend close to the distributor piston 21.
  • a distributor fuel injection pump shown in FIG. 1 for supplying a total of three injection nozzles of an internal combustion engine, in particular a diesel engine, there are a total of three guides 24, of which only one can be seen in FIG. 1.
  • radial through bores 25 are provided in the distributor cylinder 22, in each of which a pump piston 26 is guided so as to be longitudinally displaceable.
  • a so-called roller plunger 27 is guided so as to be longitudinally displaceable, which consists of a roller or roller 28 and one Pusher cup 29 exists.
  • a tappet spring 31, which is basically supported on the one hand and on a spring plate 30 resting on the bottom of the tappet cup 29, presses the tappet cup 29 against the roller 28 and the latter against the cam track 17.
  • the spring plate 30 engages behind a protruding from the radial through bore 25 Collar 26a of the pump piston 26 and thus defines the latter on the tappet cup 29.
  • Each pump piston 26 delimits a pump working chamber 32 in the radial through bore 25, the other limitation of which is formed by an annular groove 33 on the distributor piston 21.
  • a distributor groove 34 and a filling groove 35 open into the annular groove 33, each of which extends axially in opposite directions from the annular groove 33 on the distributor piston 21.
  • three injection bores 36 open in a cross-sectional plane, which are evenly distributed over the circumference of the distributor cylinder 22 and lead through the distributor cylinder 22 and the cover 11 to an injection nozzle 37 each.
  • An injection nozzle 37 of the total of three injection nozzles present is indicated schematically in FIG. 1.
  • the axial length of the distributor groove 34 is dimensioned such that it projects into the cross-sectional plane of the mouths of the injection bores 36 and thus connects one of the three injection bores 36 with the annular groove 33 depending on the rotational position of the distributor piston 21.
  • three filling bores 38 open out in the interior of the distributor cylinder 22 and are distributed uniformly around the circumference of the distributor cylinder 22.
  • the axial length of the filling groove 35 is dimensioned such that it projects into this cross-sectional plane of the mouths of the filling bores 38 and thus one of the three, depending on the rotational position of the distributor piston 21 Filling holes 38 connects with the annular groove 33.
  • the coupling of the distributor piston 21 to the drive shaft 15 takes place via a pin-slot connection, in which a driving pin is used
  • Basic position of the distributor piston 21 is determined by a helical compression spring 41, which is the end of the longitudinal groove
  • valve housing 42 of an electrical switching valve 43 On the outward-facing end face of the cover 11, the valve housing 42 of an electrical switching valve 43 is placed and fastened there in a corresponding manner.
  • the valve housing 42 engages with a centering pin in the inner cavity of the distributor cylinder 22 and, together with the opposite end face 71 of the distributor piston 21, delimits a control chamber 44 here.
  • the structure of the switching valve is known and is described, for example, in DE-OS 35 23 536.
  • the two valve connections 45, 46 of the switching valve 43 are connected to one another via a valve opening 47, which is controlled by a valve member 48.
  • the valve member 48 is actuated by an electromagnet 49, the valve member 48 opening the valve opening 47 in the non-energized state of the electromagnet 49 under the action of a return spring, not shown, and closing it in the energized state of the electromagnet 49.
  • the valve connection 45 covers a first bore section 51 of a relief line 50 opening into the end face of the cover, while the second valve connection 46 - is covered by an opening in the end face of the cover 11 of a second bore section 52 of the relief line 50.
  • the pump work chamber 32 with the pump interior 12 is located in the relief line 50 Connection.
  • the pressure line 20 between the feed pump 18 and pump interior 12 is guided via the control chamber 44 in the distributor cylinder 22, which divides the pressure line 20 into a first and a second line section 53, 54.
  • a second electrical switching valve 55 is arranged, which controls a valve opening 57 integrated in the second line section 54 with a valve member 56.
  • the valve member 56 is actuated by an electromagnet 58, the valve member 56 closing the valve opening 57 in the non-energized state of the electromagnet 58 under the action of a valve closing spring 59 and releasing the electromagnet 58 in the energized state.
  • the second switching valve 55 is controlled by a monitoring device 60, which constantly monitors the proper functioning of the first switching valve 43 and issues a closing command in the form of switching off the excitation current for the electromagnet 58 to the second switching valve 55 as soon as the valve member 48 of the first switching valve 43 despite Elimination of the excitation of the electromagnet 49 does not open.
  • a monitoring device 60 can be designed, for example, as a speed detector that issues the closing command to the second switching valve 55 when the speed of the internal combustion engine exceeds a predetermined maximum speed, which is a criterion for the no longer opening first switching valve 43.
  • the distributor piston 21 has such a rotational position that the filling groove 35 covers the filling bore 38.
  • the first switching valve 43 is open when de-energized and the second
  • Switching valve 55 is also opened by energization. Fuel now flows through the filling bore 38, the filling groove 35 and the annular groove 33 into the pump work chamber 32. After passing through the bottom dead center position of the pump piston 26, the delivery stroke of the pump piston 26 begins, the pump piston 26 becoming more inclined due to the sliding of the roller tappet 27 Flank of the cam track 17 moved radially inwards. Fuel is pumped back into the pump interior 12 from the pump work space 32 via the relief line 50 and the still open first switching valve 43. At a certain point in time during the delivery stroke, the first switching valve 43 is closed. The distributor piston 21 has reached a rotational position at the latest in which the distributor groove 34 covers an injection bore 36 and thus the
  • Pump working space 32 connects to the associated injection nozzle 37 via the injection bore 36. From the pump work space 32 fuel is now Injection nozzle 37 promoted and arrives there for injection into the cylinder of the internal combustion engine. To end the fuel injection, the first switching valve 43 is de-energized, as a result of which the opening switching valve 43 controls the pump work chamber 32 via the annular groove 33 and the
  • Relief line 50 connects to the pump interior 12.
  • the pressure in the pump work chamber 32 suddenly drops below the opening pressure of the injection nozzle 37, and the latter closes.
  • Injection nozzle 37 delivered and dosed there for fuel injection.
  • Fig. Lb the fuel injection pump is shown in the event that the first switching valve 43 is defective in such a way that its valve member 48 despite the omission of the
  • Excitation current for the electromagnet 49 does not open the valve opening 47.
  • the entire amount of fuel contained in the pump work chamber 32 reaches the injection via the injection nozzle 37 for each delivery stroke of the pump piston 26.
  • the speed of the internal combustion engine thereby increases continuously.
  • This excessive increase in the speed of the internal combustion engine is detected by the monitoring device 60 and this issues a closing command to the second switching valve 55.
  • This closing command causes the excitation current for the electromagnet 58 of the second switching valve 55 to be switched off.
  • the second switching valve closes under the action of the valve closing spring 59 55.
  • the control chamber 44 in the distributor cylinder 22 is thus from
  • bore 61 is released towards control chamber 44, so that the fuel that is still being delivered by feed pump 18 can flow back into pump interior 12 via bore 61 when second switching valve 55 is closed.
  • the second exemplary embodiment of a radial piston type distributor fuel injection pump shown in FIG. 2 differs from the fuel injection pump in FIG. 1 only in that the annular groove 33 delimiting the pump working space 32 on the distributor piston 21 is divided by an annular web 62, which has an outer diameter of the distributor piston 21 has the corresponding outer diameter.
  • the annular web 62 is placed within the annular groove 33 so that in the axial displacement position shown in FIG. 2b, assumed by the distributor piston 21 in the event of a defect in the first switching valve 43, the annular web 62 together with the inner wall of the distributor cylinder 22 form the part on the left in FIG Separates annular groove 33 from the right part of the annular groove 33 and thus from the pump working space 32.
  • the filling groove 35 opens into this now sealed part of the annular groove 33, in the axial displacement position of the distributor piston 21, the filling groove 35 is separated from the pump working area 32 in each of its rotational positions and thus the latter relative to the fuel-filled pump interior 12 cordoned off. During the suction stroke of the pump piston 26, therefore, no fuel can get into the pump work chamber 32, and the delivery of fuel from the pump work chamber 32 to the injection nozzle 37 is prevented.
  • the axial length of the filling groove 35 is shorter here or the filling bore 38 is made further away from the pump interior end of the distributor cylinder 22, so that the filling groove is in the axial displacement position of the distributor piston (Fig. 2b) 35 is not released from the distributor cylinder 22 to the pump interior 12.
  • annular groove 33 itself can be made so narrow that it is covered by the through holes 25 in the distributor cylinder 22 in the normal operating position of the distributor piston 21 (FIG. * 2a) and in the axial displacement position of the distributor piston 21 (FIG. 2b) is covered in its full length by the inner wall of the distributor cylinder 22.
  • FIG. 3 differs from the fuel injection pump in FIG. 1 in that a bypass 63 bridging the first switching valve is provided in the relief line 50 and is opened or closed by the distributor piston 21.
  • a first bypass section 64 is connected to the first bore section 51 of the relief line 50 and a second bypass section 65 is connected to the second bore section 52 of the relief line 50.
  • Each bypass section 64, 65 opens into the interior of the distributor cylinder 22. The openings are placed so that they are in the normal
  • the exemplary embodiment of a radial piston type distributor fuel injection pump shown in FIG. 4 is modified somewhat more than the exemplary embodiments in FIGS. 2 and 3 compared to the fuel injection pump in FIG. 1.
  • the pressure line 20 leading away from the feed pump 18 is directly connected to the pump interior 12.
  • the control chamber 44 in the distributor cylinder 22 is connected to the pump interior 12 via an inlet line 66 and connected via an outlet line 67 with the interposition of a throttle 68 to a drain opening 69 provided in the cover 11, which in turn is connected to the fuel tank via a fuel return line.
  • the second switching valve 55 is arranged in the inlet line 66.
  • the connection of the drive shaft 15 and the distributor piston 21 is made such that the end face 70 of the distributor piston 21 projecting into the pump interior 12 is acted upon by the fuel pressure prevailing in the pump interior 12.
  • the Monitoring device 60 controls the second switching valve 55. This closes so that no fuel can flow from the pump inner chamber 12 via the feed line 66 into the control chamber 44 'more. Only the connection of the control room 44 via the drain line 67 to the
  • FIGS. 2-4 differ from the fuel injection pump in FIG. 1 only in the modifications highlighted above. Otherwise, the structure and mode of operation are the same, so that the same reference numerals have been used for the same components. For the sake of clarity, they are
  • FIGS. 2-4 Reference numerals in FIGS. 2-4 are only entered to the extent necessary to understand the deviations from FIG. 1.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

Une pompe d'injection de carburant à distributeur comprend au moins un piston radial (26) effectuant une course d'aspiration et une course de refoulement, un piston distributeur rotatif (18) reliant des injecteurs (37) à la chambre de travail (32) de la pompe délimitée par le piston (26) et une soupape électrique de commutation (43) qui commande la quantité de carburant injecté et est en communication avec la chambre de travail (32) de la pompe et avec une chambre intérieure (12) de la pompe remplie de carburant. Afin d'assurer l'arrêt d'urgence du moteur lors d'un mauvais fonctionnement de la soupape de commutation (43), le piston distributeur (21) est axialement mobile de façon à arrêter lorsqu'il est dans une certaine position de déplacement axial le transport de carburant jusqu'aux injecteurs (37). Le piston distributeur (21) délimite avec une de ses faces frontales (71) une chambre de commande (44) connectée à une deuxième soupape électrique de commutation (55). Lorsque la deuxième soupape de commutation (55) est fermée, une supression ou une dépression par rapport à la chambre intérieure (12) de la pompe est générée et entraîne le piston distributeur (21) jusqu'à sa position axiale de déplacement.
EP19880904479 1987-06-13 1988-05-28 Pompe d'injection a distributeur du type a pistons radiaux Expired - Lifetime EP0318534B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3719807 1987-06-13
DE19873719807 DE3719807A1 (de) 1987-06-13 1987-06-13 Verteilerkraftstoffeinspritzpumpe der radialkolbenbauart

Publications (2)

Publication Number Publication Date
EP0318534A1 true EP0318534A1 (fr) 1989-06-07
EP0318534B1 EP0318534B1 (fr) 1991-07-10

Family

ID=6329656

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19880904479 Expired - Lifetime EP0318534B1 (fr) 1987-06-13 1988-05-28 Pompe d'injection a distributeur du type a pistons radiaux

Country Status (5)

Country Link
US (1) US4971012A (fr)
EP (1) EP0318534B1 (fr)
JP (1) JP2604841B2 (fr)
DE (2) DE3719807A1 (fr)
WO (1) WO1988009870A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3900318A1 (de) * 1989-01-07 1990-07-12 Bosch Gmbh Robert Verteilerkraftstoffeinspritzpumpe fuer brennkraftmaschinen
GB8918429D0 (en) * 1989-08-12 1989-09-20 Lucas Ind Plc Fuel pumping apparatus
DE3927742A1 (de) * 1989-08-23 1991-02-28 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE4032279A1 (de) * 1990-10-11 1992-04-16 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US5103792A (en) * 1990-10-16 1992-04-14 Stanadyne Automotive Corp. Processor based fuel injection control system
US5215060A (en) * 1991-07-16 1993-06-01 Stanadyne Automotive Corp. Fuel system for rotary distributor fuel injection pump
DE4135595A1 (de) * 1991-10-29 1993-05-06 Robert Bosch Gmbh, 7000 Stuttgart, De Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US5215449A (en) * 1991-12-05 1993-06-01 Stanadyne Automotive Corp. Distributor type fuel injection pump
KR940701500A (ko) * 1992-04-25 1994-05-28 클라우스 포스, 빌프리트 뵈르 내연기관용 연료 분사 장치
DE4243665C2 (de) * 1992-12-23 2003-11-13 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung, insbesondere Pumpedüse für Brennkraftmaschinen
FR2856007B1 (fr) * 2003-06-11 2005-08-26 Essilor Int Vanne et dispositif d'alimentation convenant au remplissage, avec une matiere polymerisable, d'une cavite de moulage

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3485225A (en) * 1968-04-15 1969-12-23 Caterpillar Tractor Co Rotary distributor fuel pump
GB2108727B (en) * 1980-10-29 1985-02-06 Lucas Industries Ltd Fuel injection pumping apparatus
DE3243348A1 (de) * 1982-11-24 1984-05-24 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe
DE3523536A1 (de) * 1984-09-14 1986-03-27 Robert Bosch Gmbh, 7000 Stuttgart Elektrisch gesteuerte kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3612942A1 (de) * 1986-04-17 1987-10-22 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3719831A1 (de) * 1987-06-13 1988-12-22 Bosch Gmbh Robert Kraftstoffeinspritzpumpe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8809870A1 *

Also Published As

Publication number Publication date
US4971012A (en) 1990-11-20
DE3719807A1 (de) 1988-12-22
WO1988009870A1 (fr) 1988-12-15
DE3863630D1 (de) 1991-08-14
EP0318534B1 (fr) 1991-07-10
JPH02500206A (ja) 1990-01-25
JP2604841B2 (ja) 1997-04-30

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