EP0166995B1 - Kraftstoffeinspritzpumpe für Brennkraftmaschinen - Google Patents

Kraftstoffeinspritzpumpe für Brennkraftmaschinen Download PDF

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Publication number
EP0166995B1
EP0166995B1 EP85106902A EP85106902A EP0166995B1 EP 0166995 B1 EP0166995 B1 EP 0166995B1 EP 85106902 A EP85106902 A EP 85106902A EP 85106902 A EP85106902 A EP 85106902A EP 0166995 B1 EP0166995 B1 EP 0166995B1
Authority
EP
European Patent Office
Prior art keywords
relief line
pump piston
outlet
stroke
relief
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
EP85106902A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0166995A3 (en
EP0166995A2 (de
Inventor
Werner Faupel
Klaus Schmidt
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 EP0166995A2 publication Critical patent/EP0166995A2/de
Publication of EP0166995A3 publication Critical patent/EP0166995A3/de
Application granted granted Critical
Publication of EP0166995B1 publication Critical patent/EP0166995B1/de
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
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages
    • F02M41/126—Variably-timed valves controlling fuel passages valves being mechanically or electrically adjustable sleeves slidably mounted on rotary piston

Definitions

  • the invention is based on a fuel injection pump according to the preamble of the main claim.
  • a fuel injection pump known from FR-A-2 520 812
  • the outlet of the second relief line and the outlet of the first relief line are controlled by an end face of a ring slide forming a control edge, which is adjusted on the pump piston depending on the load and speed.
  • the second relief power provided in the known fuel injection pump serves to allow only half of the pump piston delivery strokes to become effective during idling.
  • the ring slide has grooves on its end face, via which the outlet of the second relief line is opened at the start of the pressure stroke in every second delivery stroke rotational position of the pump piston when the ring slide is in the idle operating position.
  • the entry of the second relief line at the beginning of the stroke of the pump piston is connected to the first relief line, so that the fuel delivered by the pump piston can flow out via these two lines without the build-up of high pressure.
  • These two relief lines are then separated from one another when the pump piston has covered a first, defined stroke which, in the idle state, is greater than or at most the same length as the stroke which the pump piston requires to have the first outlet of the first relief line at the ring slide valve in the idle position to open.
  • the known device thus has the goal of preventing a high pressure build-up in the pump workspace at the start of the stroke of the pump piston in idle mode and at certain rotational positions of the pump piston.
  • a similar fuel injection pump is known from DE-A-3 013 087.
  • a first and a second relief channel running in the pump piston are specified there, as well as a third relief channel which branches off directly from the pump work space and is connected via a control valve controlled by a control slide to an annular groove in the lateral surface of the cylinder guiding the pump piston.
  • the first relief channel is used to discharge the amount of fuel to be delivered to the injection nozzles via a distributor bore and also has an outlet on the pump piston surface, which is controlled by a ring slide depending on the load and / or speed.
  • the second relief channel has an inlet that comes into contact with the ring groove after a certain stroke and an outlet that is also controlled by the ring slide.
  • the exit of the second relief channel is opened towards the end of the injection stroke.
  • the third relief duct has a throttling, so that fuel can flow out in a throttled manner when the connection between the pump work space and the outlet of the second relief duct is open.
  • the possibility of allowing a partial flow of the quantity delivered by the pump piston under high pressure to flow away is limited by the control of the control spool, which completely blocks the third relief channel above idle and low partial load speed. This device requires considerable effort to control the injection rate for idling and part-load or full-load operation.
  • a fuel injection pump similar to the generic type is also known, in which the connection between the first relief channel and the second relief channel is established at the start of the stroke and is only closed after a certain stroke.
  • the outlet of the second relief line is also opened during normal operation, so that the actual start of delivery only takes place when the connection between the entrance of the second relief channel and the first relief channel is interrupted. This always takes place at the same delivery strokes of the pump piston, so that a constant start of injection is achieved.
  • This initial idle stroke is also used to provide an increased amount of fuel at the start of the internal combustion engine by adjusting the ring slide controlling the exit of the second relief channel to such an extent that the exit of the second relief channel remains permanently closed.
  • an early adjustment of the start of spraying at the start is achieved in this way.
  • This configuration has nothing to do with achieving quiet running of an internal combustion engine in the low-load range.
  • FR-A-2 287 591 discloses a fuel injection pump which, similarly to the documents mentioned above, has a first relief channel and a second relief channel.
  • a second outlet of the first relief channel can be connected to the inlet of the second relief channel via an annular groove in a cylinder leading into the pump piston.
  • the first relief channel is permanently connected to the ring groove.
  • the entry of the second relief channel only comes into contact with the annular groove when the maximum delivery stroke of the pump piston has been reached.
  • the fuel injection pump according to the invention with the characterizing features of the main claim has the advantage that the fuel injection is interrupted or reduced over a constant piston stroke at idle up to part of the part-load range and there is no change in the start of injection, since in the solution according to the invention in an advantageous manner the relief takes place over a predetermined stroke section of the pump piston after a part of the delivery stroke thereof.
  • the relief is advantageously switched off by the load-dependent control of the exit of the second relief channel at higher loads or at full load.
  • a real interruption of normal fuel injection at low load is thus achieved after a pre-injection stroke. This results in an increase in the spraying duration, which produces a quiet running of the internal combustion engine, in particular when idling.
  • This device can advantageously be implemented both for quantity control by controlling the start of injection and for quantity control by controlling the end of injection.
  • FIG. 1 shows a first exemplary embodiment with control of the end of the effective injection and control of the connection of the two relief lines to one another via an annular groove
  • FIG. 2 shows a control diagram for the exemplary embodiment according to FIG. 1
  • FIG. 3 shows a second exemplary embodiment in a modification of the exemplary embodiment according to FIG Ring groove of a defined lifting height and a slot-like outlet cross section of the first relief line, which extends in the circumferential direction
  • FIG. 4 shows a third embodiment with a slot-like ring slot and an outlet cross section of the first relief line of a defined lifting height
  • FIG. 1 shows a first exemplary embodiment with control of the end of the effective injection and control of the connection of the two relief lines to one another via an annular groove
  • FIG. 2 shows a control diagram for the exemplary embodiment according to FIG. 1
  • FIG. 3 shows a second exemplary embodiment in a modification of the exemplary embodiment according to FIG Ring groove of a defined lifting height and a slot-like outlet cross section of the first relief line,
  • FIG. 5 shows a fourth embodiment with an essentially axially extending bypass channel in the Wall of the cylinder for controlling the connection of the first relief line to the second relief line
  • Figure 6 shows a fifth embodiment in modification of the embodiment of Figure 5, in which the duration d
  • FIG. 7 shows a sixth exemplary embodiment of the invention with a fuel injection pump which is designed to control the start of injection for metering fuel quantity
  • FIG. 8 shows a control diagram for the exemplary embodiment according to FIG. 7.
  • a pump piston 4 is arranged in a cylinder 2 of a cylinder liner 3 inserted into the pump housing, which is set into a reciprocating and at the same time rotating movement by means not shown.
  • the pump piston encloses a pump working chamber 5 on its one end face and partially protrudes out of the cylinder 2 into a pump suction chamber 7. It is also driven at this end of the pump piston.
  • the pump working chamber 5 is supplied with fuel via longitudinal grooves 8 arranged in the lateral surface of the pump piston and a suction bore 9 running through the cylinder liner 3 in the housing 1, as long as the pump piston executes its suction stroke or assumes its bottom dead center position.
  • the suction bore opens into the pump suction chamber 7 at its other end.
  • the pump suction chamber is supplied with fuel from a fuel tank 12 via a feed pump 11.
  • a pressure control valve 13 controls the pressure in the suction chamber in a known manner.
  • a longitudinal channel 15 leads from the working space 5 in the pump piston, which is designed as a blind bore and can be referred to as the first relief line. From this branches off a radial bore 16 which leads to a distributor opening 17 in the outer surface of the pump piston 4. In the working area of this distributor opening branch off in a radial plane of the cylinder 2 delivery lines 19, which are arranged distributed around the circumference of the cylinder according to the number of cylinders to be supplied with fuel of the associated internal combustion engine. The delivery lines 19 each lead via a valve 21, which is designed as a check valve or pressure relief valve in a known manner, to the fuel injection points, not shown.
  • a radial bore 22 branches off, which opens into a first outlet D in the lateral surface of the pump piston, specifically in the region of the part of the pump piston that projects into the pump suction chamber.
  • a quantity adjustment element in the form of a ring slide 24 is arranged on the pump piston, which can be displaced tightly on the pump piston and forms a control edge 25 with its upper end face, through which the outlet D is controlled.
  • the axial position of the ring slide 24 is determined in a known manner by a control lever 27 which can be pivoted about an axis 28 fixed to the housing and which is coupled to the ring slide via a ball head 29 at the end of its one lever arm.
  • the ring slide is adjusted by load and / or speed depending on a controller (not shown further here).
  • the ring slide 24 assumes an upper position near the pump working space, from which it is increasingly adjusted downwards as the load decreases.
  • the available useful stroke h n which the pump piston or the outlet cross section D must cover from the bottom dead center of the pump piston, thus changes in order to be opened by the control edge 25 of the ring slide.
  • a third radial bore 31 branches off from the first relief line 15 and opens into a second outlet B on the lateral surface of the pump piston 4.
  • a second relief line 33 is provided in the pump piston 4, which has an inlet A in the area of the pump piston jacket surface that is constantly located in the cylinder 2 and an outlet C in the working area of the ring slide 24. This is offset by a constant amount h " relative to the first outlet D of the first relief line towards the pump work chamber, so that the outlet C from the control edge 25 is always opened first in the course of the pump piston stroke before the first outlet D is opened.
  • annular groove 37 is arranged in the wall of the cylinder 2.
  • the inlet A and the second outlet B are assigned to one another such that when the inlet A just overlaps the bottom edge of the annular groove 37 in the course of the pump stroke of the pump piston, the second outlet B of the first relief line already overlaps with the annular groove 37 is located and after an intended stroke of the pump piston h e comes out of the overlap with the annular groove 27, a point where the inlet A of the second relief line 33 is still in overlap with the annular groove 37. In this way, a connection is established between the first relief line 15 and the second relief line 33 for the predetermined lifting section of size h e .
  • the assignment of the cross sections and control edges mentioned can be seen from the diagram in FIG. 2.
  • the assignment of the cross sections in the course of the pump piston stroke is plotted over the load or the position of the ring slide.
  • LL means idle and VL means full load.
  • the start of injection takes place, which can, for example, coincide with the start of the stroke of the pump piston from its bottom dead center.
  • the pump working chamber 5 previously filled via the suction bore 9 and the longitudinal grooves 8 is then connected to one of the delivery lines 19 via the first relief line 15, the radial bore 16, the distributor groove 17, in accordance with the rotational position of the pump piston.
  • Line C represents the opening point of the outlet C of the second relief line 33. This line rises with increasing load in accordance with the position of the ring slide 24 which is adjustable with the load. D also shows the opening point D of the first discharge line 15. This line runs parallel to line C and indicates the possible useful stroke h n . This useful stroke is indicated in FIG. 1 provided that the pump piston assumes its bottom dead center in the position shown. For the case shown, a broken position of the ring slide 24 was assumed.
  • Line SB Parallel to line SB is a line A, which marks the opening point of the inlet A of the second relief line 33.
  • the line B parallel thereto indicates the piston stroke at which the second outlet of the first relief line is closed.
  • the stroke range between A and B, the stroke h e there is a connection between the first relief line 15 and the second relief line 33. Only within this stroke range can the fuel delivered by the pump piston in this area or a part thereof flow out via the second relief line 33.
  • this is only possible with a second condition, if the outlet C of the second relief line is also open, that is to say that from the point of intersection of the line C with the line B, it is no longer possible for fuel to flow out.
  • This point G is still before the full load point, so that the entire working capacity of the pump piston can be used for fuel delivery in the upper load range and at full load.
  • the relief range between lines A and B is within the range between C and D, so that a constant amount of fuel per delivery stroke of the pump piston is initially diverted over this range until line C leads to line A. intersects at point F. Between F and G the amount of relief becomes increasingly smaller.
  • the location of the area h e and its usable height can be optimized with regard to a quiet combustion process at low load and without influencing the injection start control, which, for. B. can be done by a separate spray start adjuster of known design.
  • FIG. 3 shows another type of connection between the first relief line 15 and the second relief line 33 in a partial section of the piston.
  • the annular groove 37 has a defined height he '
  • the inlet A' of the second relief line 33 is widened in the stroke direction, so that it remains in constant communication with the annular groove 37 and the second outlet B 'of the first relief line 15 is designed in the form of a slot.
  • the second relief line 33 thus remains in constant connection with the annular groove 37.
  • the duration of the connection between the first relief line 15 and the second relief line 33 is now determined by the slot-shaped second outlet B 'during the overlap h e with the Ring groove 37 determined.
  • This embodiment has the advantage that the control times of the overlap can be made more precise here, because of the slot-like design of the second outlet B ', a rapid opening takes place, as a result of which the influence of the speed on the discharge quantity is reduced. Due to the slot-like design, a throttle cross-section can also advantageously be determined, which controls the degree of relief via the rub h e .
  • FIG. 4 shows an equivalent configuration to the exemplary embodiment according to FIG. 3. There, it is not the second outlet D but the annular groove 37 ′ which is slot-shaped and the width of the second outlet B of size h b determines the duration of the overlap h e .
  • a fourth exemplary embodiment of the connection between the first relief line 15 and the second relief line 33 is the solution according to FIG. 5.
  • a bypass channel 39 is provided there in the cylinder liner 3 and extends parallel to the axis of the pump piston.
  • the bypass channel opens into a first annular groove 41 on the pump work space and at its other end in a second annular groove 42 located on the pump suction chamber side second outlet B has overlapped with the first annular groove 41, the inlet A is only over one stroke h e overlapped with the second annular groove 42.
  • the assignment can of course also be done in the opposite sense. It is only essential that the coverage area h e is observed.
  • the annular grooves 41 and 42 can also be provided in an equivalent manner on the pump piston.
  • the embodiment according to FIG. 6 can also be carried out in such a way that the second outlet B 'of the first relief line 15 is again slit-shaped and the bypass duct 39 on the pump work chamber side, likewise in the form of a slot 44 of the same width, is realized.
  • the other end of the bypass channel 39 ' is connected to the second relief line 33 via the inlet A regardless of the pump piston stroke.
  • the width of the slot B 'or 44 determines the duration of the overlap h e .
  • the sixth exemplary embodiment according to FIG. 7 shows that the device described above for generating a quiet running of the internal combustion engine at idle and in the partial load range can also be implemented when the ring slide 24 "does not mean the end of the delivery of the pump piston to an earlier or later one Point before TDC controls, but the beginning of the delivery of the pump piston after a more or less large idle stroke of the pump piston.
  • the configuration of the fuel injection pump with pump piston 4 ', cylinder 2 and ring slide 24 is essentially the same as in the exemplary embodiment according to FIG here the ring slide is operated in reverse logic by the control lever 27. In a departure from the exemplary embodiment according to FIG.
  • the first outlet D is arranged in such a way that when the pump piston delivery stroke begins, it is first closed by the control edge 25" which is now below, before the control edge 25 "controls the subsequent outlet C" of the second relief line 33 " constructive stroke difference is also called hy here in the same way as in the exemplary embodiment according to FIG. 1, the inlet A "of the second relief line 33" and the second outlet B “of the first relief line 15" are arranged in the working area to the annular groove 37.
  • FIG. 8 shows a diagram corresponding to FIG. 2 for this embodiment.
  • the line D "runs according to the variable position of the ring slide 24" inclined towards full load VL. Tilted in the same way
  • the line C which marks the closing point of the outlet C", runs with the distance h " to the closing point line of the first outlet cross section D".
  • FE denotes a line running parallel to the abscissa, which indicates the constructive delivery end of the pump piston.
  • Line A "and line B" are also shown in the diagram as lines parallel to line FE.
  • A denotes the point at which the inlet A” comes into contact with the annular groove 37, where at the same time the connection between the second outlet B "and the annular groove 37 still exists and the line B" denotes the point at which the second Exit B "is closed and the connection between the first relief line 15" and the second relief line 33 is prevented.
  • a reduction in the resulting injection rate at idle and low load due to temporarily interrupted or reduced delivery also results in this embodiment of a fuel injection pump. Deviating from the exemplary embodiment according to FIG. 1, however, the pre-injection quantity before the relief is dependent on the load.

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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)
EP85106902A 1984-07-06 1985-06-04 Kraftstoffeinspritzpumpe für Brennkraftmaschinen Expired EP0166995B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3424883 1984-07-06
DE19843424883 DE3424883A1 (de) 1984-07-06 1984-07-06 Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Publications (3)

Publication Number Publication Date
EP0166995A2 EP0166995A2 (de) 1986-01-08
EP0166995A3 EP0166995A3 (en) 1987-06-16
EP0166995B1 true EP0166995B1 (de) 1989-03-08

Family

ID=6239970

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85106902A Expired EP0166995B1 (de) 1984-07-06 1985-06-04 Kraftstoffeinspritzpumpe für Brennkraftmaschinen

Country Status (4)

Country Link
US (1) US4635605A (nl)
EP (1) EP0166995B1 (nl)
JP (1) JPS6131628A (nl)
DE (2) DE3424883A1 (nl)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013111098B3 (de) * 2013-10-08 2014-11-13 4-QM hydraulics GmbH Strömungsmaschine

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3524241A1 (de) * 1985-07-06 1987-01-08 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3612068A1 (de) * 1986-04-10 1987-10-15 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen mit abgasrueckfuehrung
DE3644147A1 (de) * 1986-12-23 1988-07-07 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3644583A1 (de) * 1986-12-27 1988-07-07 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
EP0308988A1 (en) * 1987-09-25 1989-03-29 Sidelsky, Michael Stewart Control module
DE4106813A1 (de) * 1991-03-04 1992-09-10 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE4441505A1 (de) * 1994-11-22 1996-05-23 Bosch Gmbh Robert Kraftstoff-Förderpumpe für eine Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE19625565C2 (de) * 1996-06-26 1998-07-23 Bosch Gmbh Robert Kraftstoff-Förderpumpe für eine Kraftstoff-Einspritzpumpe für Brennkraftmaschinen
DE19713868A1 (de) * 1997-04-04 1998-10-08 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen
JP4143841B2 (ja) * 2003-09-18 2008-09-03 株式会社アドヴィックス ピストンポンプ

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2353737A1 (de) * 1973-10-26 1975-05-07 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE2448673C2 (de) * 1974-10-12 1985-12-12 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE2644698C2 (de) * 1976-10-02 1987-05-14 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe für eine Brennkraftmaschine
JPS54105616A (en) * 1978-02-06 1979-08-18 Diesel Kiki Co Ltd Distributing type fuel injection pump for internal combustion engine
DE2841807A1 (de) * 1978-09-26 1980-04-03 Bosch Gmbh Robert Einrichtung zum regeln des mengenverhaeltnisses luft/kraftstoff bei brennkraftmaschinen
JPS56545A (en) * 1979-06-14 1981-01-07 Diesel Kiki Co Ltd Distributing type fuel injector
DE3013087A1 (de) * 1980-04-03 1981-10-15 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer selbstzuendende brennkraftmaschinen
DE3203582A1 (de) * 1982-02-03 1983-08-11 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
JPS5982572A (ja) * 1982-11-01 1984-05-12 Nissan Motor Co Ltd 分配型燃料噴射ポンプの多段階噴射装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013111098B3 (de) * 2013-10-08 2014-11-13 4-QM hydraulics GmbH Strömungsmaschine
WO2015051784A2 (de) 2013-10-08 2015-04-16 4-QM hydraulics GmbH Strömungsmaschine

Also Published As

Publication number Publication date
JPS6131628A (ja) 1986-02-14
JPH0577856B2 (nl) 1993-10-27
EP0166995A3 (en) 1987-06-16
US4635605A (en) 1987-01-13
EP0166995A2 (de) 1986-01-08
DE3424883A1 (de) 1986-02-06
DE3568608D1 (en) 1989-04-13

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