EP0150471A2 - Pompe d'injection de combustible - Google Patents

Pompe d'injection de combustible Download PDF

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Publication number
EP0150471A2
EP0150471A2 EP84116075A EP84116075A EP0150471A2 EP 0150471 A2 EP0150471 A2 EP 0150471A2 EP 84116075 A EP84116075 A EP 84116075A EP 84116075 A EP84116075 A EP 84116075A EP 0150471 A2 EP0150471 A2 EP 0150471A2
Authority
EP
European Patent Office
Prior art keywords
pump
fuel
fuel injection
piston
distributor
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
EP84116075A
Other languages
German (de)
English (en)
Other versions
EP0150471A3 (en
EP0150471B1 (fr
Inventor
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 EP0150471A2 publication Critical patent/EP0150471A2/fr
Publication of EP0150471A3 publication Critical patent/EP0150471A3/de
Application granted granted Critical
Publication of EP0150471B1 publication Critical patent/EP0150471B1/fr
Expired legal-status Critical Current

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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
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06—Pumps peculiar thereto
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing

Definitions

  • the invention is based on a fuel injection pump according to the preamble of the main claim.
  • a fuel injection pump of this type known from DE-PS 18 07 554, the fuel injection pump is designed as a reciprocating piston distributor pump with a relief channel which runs in the pump piston and branches off from the pump work space and has a lateral outlet on the pump piston and from a certain stroke position of the same with the respective pump delivery stroke with a relief line is connected, which is connected via a variable and a fixed throttle with a relief volume of constant content.
  • the capacity of this volume is determined on the one hand by the variable throttle, which is adjustable depending on the load, and on the other hand by the fixed throttle, which acts as a function of the speed.
  • the known device does not allow universal use and it In particular, the amount of a pre-injection before the actual main injection and the time interval between the pre-injection and the main injection cannot be determined over wide operating ranges of the internal combustion engine.
  • the fuel injection pump with the characterizing features of the main claim has the advantage that a desired distance of the pre-injection before the main injection can be set sufficiently accurately in wide operating ranges of the internal combustion engine with the help of the adjustable fuel removal volume.
  • the point in time at which the connection between the pump chamber and the fuel extraction chamber is opened determines the amount of the pre-injection, which in turn depends on geometric variables that are independent of the speed and can be set with sufficient accuracy for wide operating ranges of the internal combustion engine.
  • the configuration according to claims 4 to 4 also offers the possibility of precisely controlling the amount of the pre-injection as a function of operating parameters and also of changing it during operation of the fuel injection pump.
  • the fuel injection pump according to the invention can also be implemented on a radial piston pump without significant effort, according to claim 9.
  • FIG. 1 shows the first exemplary embodiment in longitudinal section
  • FIG. 2 shows a partial section through the injection pump according to FIG. 1 perpendicular to the sectional plane shown there
  • FIG. 3 shows a development of the distributor according to FIG. 1 together with the lateral surfaces surrounding it
  • FIG. 4 shows part of the cam elevation curve of the cam drive 1 with an assigned injection quantity curve over the angle of rotation
  • FIG. 5 shows a partial development of the distributor and the circumferential surface surrounding it from a further development of the exemplary embodiment according to FIG. 1
  • FIG. 6 shows a second exemplary embodiment in use with an in-line or reciprocating piston injection pump
  • FIG. 7 8 shows a third embodiment, also in use with a reciprocating piston or in-line injection pump with an adjustable trigger point of the removal space
  • FIG. 9 shows a modification to the embodiment according to FIGS. 1, 2 and 8.
  • a distributor 3 is mounted in a bore 2 and is driven at a pump speed by a drive (not shown further here).
  • the distributor can be coupled at its end to a cam ring carrier 7 via a pin 5 guided through a longitudinal groove 4 provided there, which is approximately cup-shaped and carries a cam ring 8 with a radially inwardly directed cam track 9 on its upper edge. In this way, the cam track and distributor are moved synchronously with one another, the distributor being displaceable in the longitudinal direction by a drive (not shown further here).
  • the distributor has an annular groove 11 on its outer surface, which is in constant connection with one or is a plurality of pump piston guide bores 12 extending radially from the bore 2, in which pump pistons 14 are arranged, which enclose with their end face a working space 15 to the side of the annular groove 11.
  • Roller plungers 17, which are in contact with the cam track 9 via rollers 18, are guided coaxially with the pump pistons in an adjacent bore 16 with a larger diameter than that of the guide bore 12. By relative movement of the same, the pistons are set in a reciprocating, pumping and sucking movement.
  • a first control groove 20 and a second control groove 21 branch off from the annular groove 11, which are worked into the surface of the distributor and initially move away from one another in the manner of a V, starting from the annular groove.
  • the second control groove 21 is longer and merges into an axially parallel part 22, which finally opens into a rectangular control surface 23.
  • In the area of the control surface there are outlets of injection lines 25 into the bore 2 within a radial plane distributed around the circumference of the distributor, the injection lines being arranged according to the number and distribution of the combustion chambers to be supplied to the associated internal combustion engine.
  • a plurality of control openings 27 are provided in the lateral surface of the bore 2 in a radial plane, which are connected via lines 28 to a fuel storage space 30.
  • This is supplied in a known manner by a fuel feed pump, not shown here, with fuel which is kept at a relatively low pressure level.
  • the distribution of the control openings 27, the are distributed according to the number of fuel injection lines to be supplied distributed around the circumference, the development according to Figure 3 can be seen. They have an approximately trapezoidal cross-section such that the side flanks are opened and closed across the entire width by the first control groove 20 or second control groove 21, each running at the same angle.
  • the distributor 3 has an end part 35 protruding from the bore 2, on which an annular slide 36 is placed, from the inner bore 37 of which a channel 38 radially leads away, which leads into a cylinder 40 incorporated in an extension 39 of the annular slide Piston 41 slidably arranged as a movable wall, which is loaded on its rear side by a return spring 42 and includes on its front side a fuel removal space 43 which is connected to the channel 38.
  • the working path of the piston 41 can be limited by an adjustable pin 45, which is used as an adjustable stop coaxially with the return spring 42.
  • the distributor In the area of the ring slide, the axial position of which can be fixed, the distributor has relief openings in the form of longitudinal grooves 46, which are axially parallel according to the development of Figure 3. These longitudinal grooves are also arranged according to the number and distribution of the injection lines 25 on the circumference of the distributor and are connected to one another via radial bores 49, which in turn are connected to the control surface 23 or to the annular groove 11 or the pump working chamber 15 via a pressure channel 50 in the distributor.
  • the injection pump shown in this example is a pump for supplying a six-cylinder internal combustion engine with six injection lines 25.
  • two first control grooves 20 and two second control grooves 21 are provided here, whereby however, only one of the second control grooves has the control surface 23.
  • the filling of the pump work spaces has just been completed and the effective delivery cycle of the pump pistons begins.
  • the control surface 23 is in register with one of the injection lines 25, into which fuel is subsequently conveyed.
  • the just effective longitudinal groove 46 connected to the control surface 23 has not yet overlapped with the channel 38 branching off from the inner bore 37.
  • a pre-injection according to FIG. 4 is initially carried out over the area ⁇ , which the distributor has to rotate further in order to bring the longitudinal groove 46 into overlap with the channel 38.
  • the cam rise of a cam of the cam track is shown with a roller tappet 17, which opens the cam web rolls off. Apply on the cam track, the stretches are drawn out for which the pre-injection VS and the main injection HS take place. The injection quantities are plotted against the cam angle under the cam elevation curve.
  • the first control grooves 20 also overlap with the control openings 27, so that a sufficiently large filling cross section is available during the subsequent suction stroke of the pump pistons. Fuel can get into the pump work space both via the first control grooves and via the second control grooves when the control openings 27 and inlet cross sections 33 are open.
  • the trailing boundary edge of the second control grooves 21, which are inclined in the direction of rotation are the first ones which determine the start of injection Control edges are to be referred to, while the leading boundary edges of the first control grooves 20 inclined in the opposite direction of rotation are to be referred to as the second control edges 52 which determine the end of the spray.
  • the distance between the first control edge 51 and the second control edge 52 in the region of the radial plane of the control openings 27 thus determines the injection quantities which, due to the inclined arrangement of the control grooves, can be changed by axially displacing the distributor.
  • the angular distance between the pre-injection VS and HS is influenced by the swallowing volume of the fuel removal space 43, which can be adjusted by adjusting the pin 45.
  • the amount of the pre-injection is, as already mentioned, determined by the angle of rotation ⁇ , which, according to the configuration according to FIG.
  • the relief openings or longitudinal grooves 46 are arranged obliquely to the axis of the distributor, the preferably rectangular configuration of the connecting cross section of the channel 38 being adapted to this oblique position with its lateral orientation.
  • FIG. 2 Another embodiment variant is shown in Figure 2, where the ring slide 36 is rotatable with axial fixation by means of a z. B. electrically controlled actuator 54.
  • the point can be varied at which the relief opening 46 connects the pump work space with the fuel removal space. Additional influences on the pre-injection quantity are possible here as a function of further parameters, regardless of the above-mentioned mode of operation.
  • the relief openings used in a radial piston pump can also be designed as inclined longitudinal grooves 46. Instead of a rotary drive, a stroke drive or an axial displacement of the ring slide is also possible, in which case the longitudinal grooves 46 must be inclined in order to effect the adjustment of the pre-injection quantity.
  • This version can be implemented in reciprocating injection pumps. Which is ultimately also applicable to in-line pumps.
  • FIG. 6 shows an application of the exemplary embodiment in a series pump or in a piston injection pump.
  • a series injection pump only one pump piston 56 is shown, which in a generally known manner is set into a reciprocating pumping movement by a cam of a cam drive shaft.
  • the pump piston encloses a pump working chamber 58 in a pump cylinder 57.
  • an injection line 60 leads via a pressure valve 59 to an injection valve 61 assigned to one of the cylinders of the internal combustion engine.
  • a filling and relief line 63 which is connected to a fuel supply pump, opens into the pump cylinder 57.
  • the opening 64 of this filling and relief line is controlled by the end face 66 of the pump piston, which delimits the pump working space 58, or by a control edge on this end face, such that the suction chamber of the pump piston at the bottom dead center at the latest, the work space via the filling and relief line 63, which is now open, is filled with fuel.
  • the effective delivery stroke of the pump piston begins when this line is closed.
  • the pump piston has, in a known manner, an annular groove 68, the boundary edge of which on the pump work chamber side is formed as an inclined control edge 69.
  • the annular groove 68 is in constant communication with the pump work space via a longitudinal groove 70.
  • the pump piston After the start of the effective delivery stroke or after closing the filling and relief line, the pump piston effectively delivers fuel under high pressure into the injection line 60 until the oblique control edge 69 opens the filling and relief line 63 again, so that the pump working space is relieved via the longitudinal groove 70 and the annular groove 68 to the filling and relief line 63 can take place. With that, the high pressure funding is under broken and the injection ended.
  • the pump piston has a generally known turning device (not shown further here), with which the assignment of the control edge 69 to the mouth of the filling and relief line 63 can be varied and the effective delivery stroke or the fuel injection quantity can be controlled.
  • a channel 72 opens into the pump cylinder 57, which leads to a fuel removal space 73 which is enclosed in a cylinder 75 in the same way as in the exemplary embodiment according to FIG. 2 or by a piston 74.
  • the piston is acted upon by a return spring 76 on the side facing away from the fuel removal space 73 and can be deflected over a maximum distance from the amount ⁇ from its rest position to an adjustable stop 77.
  • a piston it is also possible, as in the preceding examples, to implement another form of movable wall which encloses the fuel removal space 43 or 73.
  • the mouth of the channel 72 in the pump cylinder 57 is placed so that the connection to the annular groove 68 is established after a pump piston stroke of the amount ⁇ after the filling and relief line 63 has been closed.
  • the pump piston additionally delivers fuel into the fuel removal chamber 73 until the receiving volume is exhausted in accordance with the evasive movement of the piston 74.
  • the result is a similar characteristic of the injection process as described in previous examples in FIG. 4.
  • the position of the channel 72 cannot be changed, but a load-dependent influencing of the size of the pilot injection in accordance with the partial stroke ⁇ can be produced by controlling the opening of the channel T2 as shown in FIG edge 69 is assigned that depending on the rotational position of the pump piston, the connection between channel 72 and annular groove 68 is made after a shorter or longer initial stroke of the pump piston.
  • a second rotational position of the piston is shown in dashed lines in FIG. The control edge 69a results.
  • a pump piston 81 of the injection pump is shown here, which is set in a pump cylinder 82 in a reciprocating, conveying and suction pumping movement.
  • This pump piston also has an annular groove 83, with the one boundary edge as control edge 84 controlling the mouth of a filling and relief line 85.
  • This is also controlled by a control edge 86 on the front side 87 of the pump piston for controlling the suction process or filling process of the pump work chamber 88 and the start of the effective fuel delivery after the filling and relief line 85 has been closed by the control edge 86
  • Radial bore 90 extending from an axial bore 89 in the pump piston in connection with the pump work chamber 88.
  • a part of the pump piston protrudes into a space 91 inside the fuel injection pump.
  • the pump piston carries a ring slide 92 arranged on it in the same way as the ring slide 36 according to the exemplary embodiment according to FIGS. 1 and 2.
  • a channel 95 which corresponds to the channel 38 in FIG. 3, branches off from the inner bore 93 through which the pump piston is tightly guided .
  • This opens into a fuel removal space 96, which is enclosed in a cylinder 97_ by a piston 98 which can be moved there tightly.
  • the piston in turn is loaded on its rear side by a return spring 99 and can move against the force of this spring by an amount ⁇ up to an adjustable stop 100.
  • the pump piston In the area of the inner bore 93, the pump piston has an oblique groove 101, in which the axial bore 89 starting from the end face 86 ends.
  • the ring slide is adjustable in the same way as in the exemplary embodiment according to FIGS. 1 and 2 by an adjusting device and can either be axially displaced, rotated or adjusted in both directions, depending on the configuration of the adjusting device and the parameters to be taken into account.
  • the inclined position of the groove 101 allows, for example, a pure rotation of the ring slide 92, so that a larger or smaller pre-injection stroke ⁇ becomes effective through the rotation of the ring slide and / or the rotation of the pump piston, depending on its load position, until the connection between the channel 95 and the ring groove 101 is manufactured.
  • a load-dependent influence on the injection process can be exerted.
  • this can also be compensated for in a targeted manner by rotating the ring slide accordingly. Additional influences can be made via an axial adjustment of the ring slide.
  • the corresponding stop can be designed as a bolt 103 which plunges coaxially into the cylinder 42 and whose immersion depth is controlled by an electrically controlled adjusting device 104. In this way, the amount 4 or the distance can be during operation

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
EP84116075A 1984-01-11 1984-12-21 Pompe d'injection de combustible Expired EP0150471B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3400612 1984-01-11
DE3400612 1984-01-11
DE3444234 1984-12-05
DE19843444234 DE3444234A1 (de) 1984-01-11 1984-12-05 Kraftstoffeinspritzpumpe

Publications (3)

Publication Number Publication Date
EP0150471A2 true EP0150471A2 (fr) 1985-08-07
EP0150471A3 EP0150471A3 (en) 1985-08-21
EP0150471B1 EP0150471B1 (fr) 1988-07-27

Family

ID=25817470

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84116075A Expired EP0150471B1 (fr) 1984-01-11 1984-12-21 Pompe d'injection de combustible

Country Status (3)

Country Link
US (1) US4696271A (fr)
EP (1) EP0150471B1 (fr)
DE (2) DE3444234A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0315564A1 (fr) * 1987-11-02 1989-05-10 Stanadyne Automotive Corp. Pompe-injecteur combinée à commande électronique
EP0406592A2 (fr) * 1989-07-06 1991-01-09 Robert Bosch Gmbh Pompe à injection de combustible
EP0736685A2 (fr) * 1995-04-03 1996-10-09 Zexel Corporation Pompe distributrice d'injection de carburant

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3722265A1 (de) * 1987-07-06 1989-01-19 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
EP0325376A3 (fr) * 1988-01-16 1989-11-15 LUCAS INDUSTRIES public limited company Dispositif de pompage de combustible
US4951626A (en) * 1988-02-10 1990-08-28 Robert Bosch Gmbh Electrically controlled fuel injection pump
GB8923485D0 (en) * 1989-10-18 1989-12-06 Lucas Ind Plc Fuel pumping apparatus
GB8923487D0 (en) * 1989-10-18 1989-12-06 Lucas Ind Plc Fuel pumping apparatus
US5098260A (en) * 1990-04-23 1992-03-24 Cummins-Engine Company, Inc. Position-servo device for positioning a stop in a positive displacement fuel injection system
US5133645A (en) * 1990-07-16 1992-07-28 Diesel Technology Corporation Common rail fuel injection system
US5230613A (en) * 1990-07-16 1993-07-27 Diesel Technology Company Common rail fuel injection system
DE4037165A1 (de) * 1990-11-22 1992-05-27 Kloeckner Humboldt Deutz Ag Kraftstoffeinspritzpumpe mit voreinspritzung
DE4137072A1 (de) * 1991-11-12 1993-05-13 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US5257606A (en) * 1992-06-23 1993-11-02 Carter Automotive Company, Inc. Fuel pump accumulator
GB9317615D0 (en) * 1993-08-24 1993-10-06 Lucas Ind Plc Fuel pump
CN103644054B (zh) * 2013-12-05 2016-03-30 中国第一汽车股份有限公司无锡油泵油嘴研究所 分层式燃油分配器

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE585014C (de) * 1932-06-22 1933-09-27 Robert Bosch Akt Ges Einspritzpumpe fuer Brennkraftmaschinen mit Voreinspritzung
FR2067883A5 (fr) * 1969-11-20 1971-08-20 Peugeot
FR2093250A5 (fr) * 1970-06-08 1972-01-28 Peugeot
DE3224152A1 (de) * 1982-06-29 1983-12-29 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2055578A (en) * 1930-05-29 1936-09-29 Bosch Robert Fuel supply and regulating system for internal combustion engines
GB507940A (en) * 1938-02-05 1939-06-23 Austin Motor Co Ltd Improvements in or relating to internal combustion engines of the compression ignition type
US2250877A (en) * 1939-05-19 1941-07-29 Kloeckner Humboldt Deutz Ag Fuel injector for internal combustion engines
US2810375A (en) * 1953-04-13 1957-10-22 Nordberg Manufacturing Co Injection pump for internal combustion engines
US3456629A (en) * 1966-08-01 1969-07-22 Peugeot Fuel injection devices for compression ignited internal combustion engines
GB1180630A (en) * 1966-08-01 1970-02-04 Peugeot Improvements in or relating to Fuel Injection Devices for Compression Ignited Internal Combustion Engines
GB1265490A (fr) * 1968-08-13 1972-03-01
FR2071175A5 (fr) * 1969-12-19 1971-09-17 Peugeot
JPS51120321A (en) * 1975-04-14 1976-10-21 Yanmar Diesel Engine Co Ltd Fuel injection pump for diesel engine
MX154828A (es) * 1981-12-24 1987-12-15 Lucas Ind Plc Mejoras en un sistema de inyeccion de combustible para un motor de combustion interna
US4505244A (en) * 1982-05-06 1985-03-19 Cummins Engine Company, Inc. Fuel injection system

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE585014C (de) * 1932-06-22 1933-09-27 Robert Bosch Akt Ges Einspritzpumpe fuer Brennkraftmaschinen mit Voreinspritzung
FR2067883A5 (fr) * 1969-11-20 1971-08-20 Peugeot
FR2093250A5 (fr) * 1970-06-08 1972-01-28 Peugeot
DE3224152A1 (de) * 1982-06-29 1983-12-29 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0315564A1 (fr) * 1987-11-02 1989-05-10 Stanadyne Automotive Corp. Pompe-injecteur combinée à commande électronique
EP0406592A2 (fr) * 1989-07-06 1991-01-09 Robert Bosch Gmbh Pompe à injection de combustible
EP0406592A3 (en) * 1989-07-06 1991-09-04 Robert Bosch Gmbh Fuel injection pump
EP0736685A2 (fr) * 1995-04-03 1996-10-09 Zexel Corporation Pompe distributrice d'injection de carburant
EP0736685A3 (fr) * 1995-04-03 1997-03-19 Zexel Corp Pompe distributrice d'injection de carburant

Also Published As

Publication number Publication date
US4696271A (en) 1987-09-29
DE3444234A1 (de) 1985-07-18
EP0150471A3 (en) 1985-08-21
DE3473005D1 (en) 1988-09-01
EP0150471B1 (fr) 1988-07-27

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