EP0678166B1 - Dispositif de commande pour une pompe a volume de remplissage variable - Google Patents

Dispositif de commande pour une pompe a volume de remplissage variable Download PDF

Info

Publication number
EP0678166B1
EP0678166B1 EP94930902A EP94930902A EP0678166B1 EP 0678166 B1 EP0678166 B1 EP 0678166B1 EP 94930902 A EP94930902 A EP 94930902A EP 94930902 A EP94930902 A EP 94930902A EP 0678166 B1 EP0678166 B1 EP 0678166B1
Authority
EP
European Patent Office
Prior art keywords
displacement
valve
control device
pressure
pump
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 - Lifetime
Application number
EP94930902A
Other languages
German (de)
English (en)
Other versions
EP0678166A1 (fr
Inventor
Wolfgang Schneider
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.)
CRT Common Rail Technologies AG
Original Assignee
Schweizerische Industrie Gesellschaft
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=25678018&utm_source=***_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0678166(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Schweizerische Industrie Gesellschaft filed Critical Schweizerische Industrie Gesellschaft
Publication of EP0678166A1 publication Critical patent/EP0678166A1/fr
Application granted granted Critical
Publication of EP0678166B1 publication Critical patent/EP0678166B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • 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
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • 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
    • F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment
    • 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
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/365—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages valves being actuated by the fluid pressure produced in an auxiliary pump, e.g. pumps with differential pistons; Regulated pressure of supply pump actuating a metering valve, e.g. a sleeve surrounding the pump piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D41/3809—Common rail control systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2205/00—Fluid parameters
    • F04B2205/06—Pressure in a (hydraulic) circuit
    • F04B2205/062—Pressure in a (hydraulic) circuit before a throttle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2205/00—Fluid parameters
    • F04B2205/08—Pressure difference over a throttle

Definitions

  • the present invention relates to a control device for at least one displacement room Liquid displacement pump according to the preamble of Claim 1.
  • EP-A-0 299 337 there is an injection system for Internal combustion engines described a high pressure positive displacement pump having. To at a constant pump speed the amount of hydraulic fluid delivered by the pump the inflow to the Displacement pump limited. A controlled one serves this purpose Throttle device, the upstream of the displacement space Pump is arranged in the supply line to the displacement chamber.
  • Throttle device the upstream of the displacement space Pump is arranged in the supply line to the displacement chamber.
  • the present invention is based on the object a control device that is inexpensive to manufacture to create the generic type, which at low Effort to create cavities or gas volumes at least in the flow path of the liquid to be pumped is able to avoid significantly.
  • Control device can be the dependent claims remove.
  • FIG. 1 shows a first possible embodiment of a control device for a pump with automatic inlet valves.
  • the pump according to the schematic representation of FIG. 1 has three individual displacement pistons 9, of which only one can be seen in FIG. 1.
  • the three displacers become driven by a rotary shaft 12 via respective eccentric 11, each eccentric 11 arranged in a lifting member 10 is that at the lower end of the associated piston 9th located.
  • the rotary movement A of the eccentric 11 initiates in this case an oscillating movement B, wherein the piston 9 as Displacer in the displacement space 15 between the two Dead center positions C (bottom dead center) and D (top dead center) moved back and forth and triggers the periodic suction movement.
  • the piston does not rise in any phase due to the lifting member 10 its movement from the eccentric 11 (positive displacement movement).
  • the flow rate through each displacer is determined by a respective, upstream, throttling, spring-loaded 2/2-way valve 21 and by a Adjustment device 27, which in this example as Adjusting throttle 30 is formed, determined.
  • the adjusting device 27 like the adjusting device 27a and 27b of the same design, is fed by a common line 32, which provides the liquid to be pumped, here diesel oil, with a pressure p2.
  • the diesel fuel 2 comes from a liquid reservoir 1, where it is in contact with a gas 3 at a pressure p 1, here air at atmospheric pressure p1, at a contact surface 4.
  • the liquid can become saturated with gas.
  • the liquid initially flows through a system 7, in which preferably no further gas is to be added to the liquid. Since the pressure is to be increased from p1 to p2, a pressure-increasing device, ie a pressure source 8, is integrated in the system 7 in this example.
  • the diesel liquid then flows in line 32 the three adjusting throttles 30, 30a, 30b and the associated throttles differential operated, throttling 2/2-way valves 21, 21a and 21b. Because of the continuity equation for incompressible media (which is only due to the absence of voids can be assumed) is the flow rate through each variable throttle and the 2/2-way valve assigned to it 21, 21a and 21b, respectively. From this arises Equilibrium state from the pressure p3 on the active surface 24 of the 2/2-way valve 21 on one side and a reservoir-like one Pressure p12 close to p1 on the active surface 23 the other side of the 2/2-way valve and from the Force of the spring 22 a.
  • the variable throttles 30, 30a, 30b can theoretically be adjusted individually or be coordinated.
  • valve active surfaces 24, 24a, 24b and the associated throttles 30, 30a, 30b the system has an inherent damping effect, which increases with greater throttling, which is important for the maintenance and reproducibility of the delivery characteristics (see FIGS. 10 and 11).
  • the damping works by already having a slight overshoot of the throttling 2/2-way valves 21, 21a, 21b in the suddenly opening phase the volume increase generated by the product of surface 24, 24a, 24b and stroke difference in the connection 31, 31a, 31b Lowering of the pressure p 3 by a considerable ⁇ p 3 counteracting the overshoot - because of the low level of voids achieved according to the invention!
  • the pressure difference operated throttling 2/2-way valves 21, 21a and 21b are each on in this exemplary embodiment its active surface 23 connected to the return 6, whereby the reservoir-like pressure p12 near p1 on the active surface 23 prevails.
  • This arrangement has the advantage that the spring 22 - depending on Size of the area 23 - can be chosen very weak and less the pretensioning than the regulating Resetting the valve (21) against the opening pressure p3 serves on the other active surface 24, since with the pressure p12 the effective area 23 already a considerable part of the necessary bias and maybe even more.
  • FIG. 2 shows a similar control device to FIG. 1 , with the difference that the pump inlet slots 35th has and only one central adjustment device 27 is provided is, which has an adjusting throttle 30. Pumps with In contrast to those, inlet slots can be used with As a rule, manufacture inlet valves more cheaply, while their application focus is less at the highest Press and thin fluid media.
  • the low cost goal comes in this embodiment the central adjustment device 27, which is fundamentally a simple manual adjustment or an electric one Adjustment allowed.
  • the single variable throttle 30 in the adjusting device 27 can be known in a conventional manner Represent way also inexpensively.
  • the pressure difference p2-p3 through the variable throttle a pressure differential valve 40 connected in parallel independent of the flow rate, kept approximately constant, whereby themselves in the combination of the variable throttle 30 and Differential pressure valve 40 the effect of a flow control valve results.
  • the simplicity, for all displacement elements 16, 16a, 16b to use the same variable throttle 30 results further advantages in this constellation with the inlet side Slit control of the pump.
  • a first advantage is that the control cross section of the Throttle 30 for a certain speed and certain Relative displacement filling from the number of served displacement rooms as well from the brevity of the respective suction phases ago much larger than for example in the case of the individual chokes in the constellation 1 is. (Assumption of the same speed and the same relative filling).
  • a second advantage is that due to the short suction phases and even phase displacement of the displacement movement a Overlap of the suction phases is relatively slight or not at all is available. (There is an overlap of the suction phases not present if the height of the opening 35 is so low is held that the swept area angular area of the eccentric 11 or the rotary shaft 12 during the release the opening 35 through the piston 9 a maximum of 360 ° / number Displacement elements).
  • a third advantage arises when the release angle described a certain amount smaller than the 360 ° / number of displacement elements is. Then there are more or less short intermediate phases in which none of the displacement rooms sucks.
  • the filling of the channel pieces 36, 36a, 36b between the respective 2/2-way valve 21, 21a, 21b and the respective Inlet cross sections 35 (35a, 35b covered, not visible in the drawing) can basically between the suction phases go on. This also helps in the channel pieces 36, 36a, 36b, d. H. up to the displacement space limit in the form of the Inlet cross section 35 at least one cavity cavity to reach.
  • the pressure p 3 in the connecting channels can even rise to a maximum of p 2 , since no fluid is removed from the channel pieces 36, 36a, 36b by any suction element. This leads to a temporary larger opening of the 2/2-way valves and to an acceleration of the filling of the duct sections.
  • Fig. 3 represents a particularly favorable form of training Control device of FIG. 1.
  • the adjustment device 27 is even in this example connected to the pump by hose lines 41, 41a, 41b, what a remote control possibility of the pump over a multiple length of the characteristic pump dimension (e.g. Diameter with a radial piston pump).
  • FIG. 3 shows a further possible and advantageous variant of the invention, as an additional Damper inherent to that described above in FIG. 1 Damping added.
  • the damper shown is only an example for possible designs.
  • the respective pressure difference actuators throttling 2/2-way valves 21 are in this Example connected to respective damping pistons 73, which. in respective cylinders 70 according to the movement of the Slider of the 2/2-way valves 21 are reciprocable.
  • the effect of damping is due to the lack of voids.
  • Attenuation chambers 71 and 72 are in the respective cylinders 70 on opposite sides of the respective damping piston 73 is formed.
  • FIG. 4 and 5 show in cross section and in longitudinal section Particularly favorable design example of a pump with a control device according to the invention.
  • the pump according to Fig. 4 and 5 is equipped with four displacement spaces 129a-d, the pairs above and below the drive shaft 110 are arranged.
  • the displacement space 129b is in FIG. 5 not seen since he is behind the cutting plane (V-V in Fig. 4) is in the upper part of the drawing.
  • the displacers 117 are by respective springs 135 in contact with two on the drive shaft 110 eccentrically mounted drive rings 114 in Kept in touch.
  • the drive rings 114 are by means of Needle bearings 115 are rotatably mounted on eccentrics 113 offset from one another with the drive shaft 110 in a rotationally fixed manner are connected.
  • the springs 135 for the respective displacement pistons 117 are supported on a plate-shaped abutment 116 at the end every single displacement piston and the drive ring 114 presses on the respective displacement piston 117 opposite sides of the spring abutment 116.
  • the Rotation of the drive shaft 110 therefore causes the over their non-rotatably connected eccentric 113 and the rings 114 one
  • the reciprocating piston 117, the Stroke movement of the upper displacement piston 117 offset by 180 ° to the lifting movement of the opposite lower one Displacement piston 117 takes place.
  • the two eccentrics 113 are 90 ° offset from each other connected to the rotary shaft 110, so that the stroke phase difference of two arranged side by side Displacement piston 117, i.e. from the lower displacement pistons 117 in Fig. 5 and the upper displacement piston also 90 ° is. On the one hand, this contributes to the smooth running of the Pump, on the other hand, for an even supply of liquid at.
  • the rotary shaft 110 is in the main housing 138 of the pump Ball bearing 136 and the roller bearing 137 rotatably supported.
  • each displacement space 129a-d (of which the displacement space 129c is not shown) is a respective intake valve 134 and a respective outlet valve 118 are provided.
  • the respective inlet and outlet valve pairs 134, 118, which too belong to the respective displacement spaces 129a-d are in respective housing parts 133a-133d housed in which also those that form the displacement spaces 129a-d and the recording the displacement piston 117 serving cylinder are.
  • These housing parts 133a-d each have a cylindrical one Extension which is coaxial to the respective cylinder, i.e. arranged to the respective displacement piston 117 and in one corresponding cylinder bore of the main housing part 138 is used.
  • each Housing part 133a-d and the housing 138 is one respective ring seal, so that the main housing 138 against Leak is sealed.
  • the cylindrical extension of each Housing part 133a-d also has an annular shoulder, at the end facing away from the plate-shaped abutment 116 the respective spring 135 is supported. I.e. the ring shoulder forms another abutment for the spring 135.
  • Each housing part 133a-133d is also provided with a respective one Valve cover 119a-d provided, the individual valve covers 119a-d a respective cylindrical recess 121 have coaxial with the cylindrical extension of the each assigned housing part 133a-d is arranged and a stem portion of intake valve 134 and those cooperating therewith Receives components that in Figs. 6A and 6B in are shown on an enlarged scale.
  • the valve cover 119a-d and the housing parts 133a-d are continuous Screws shown in Fig. 5 with the Screwed crankcase 138.
  • valve 150 provides in this embodiment the adjustable element that is used to control the pressure-differential operated, throttling 2/2-way valves, which in this embodiment through the respective intake valves 134 are formed with the associated parts, such as is described in more detail later.
  • each Distribution route 130a-d are located in the respective Cylinder heads 119a-d respective oblique bores 127a-d, which open into the cylindrical spaces 121, whereby the oblique bores 127c and 127d are not shown.
  • the hollow rotary slide valve 150 receives which in this example is an easily replaceable one Insert cartridge is formed in the direction of arrow E over a housing bore 132 liquid from a reservoir 1 with the pressure p2, as shown for example in FIG. 3 is.
  • the fluid advances without significant pressure loss in the interior of the hollow rotary valve over one constantly open, sufficiently large inlet cross-section 156 Rotation of the hollow rotary valve, which is done by means of an electric Drive 158 (Fig.
  • valve cartridge on the not shown The back of each chamber is symmetrically opposite have the same openings 155a-155d and 156 and the movable one Slider be made very thin-walled, so that the valve has the advantages of a valve according to DE-C 37 14 691.
  • the pressure p3 in the distribution lines 130a to 130d becomes via the oblique bores 127a-d in the respective cylinder rooms 121 communicates and acts here across the cross-sectional area of the stem of the valve 134 in the opening direction on the Valve 134 on.
  • valve 134 When valve 134 is closed the same pressure p3 also acts in the opening direction of the valve on the side of the valve head facing the chamber 134 a-d a.
  • the two springs 125 and 126 practice one at this stage Closing force on the valve 134.
  • valve 134 When enlarging the respective displacement room 129a-d by moving the respective displacer away from top dead center (OTP), prevails on the Positive side of valve 134 is a lower pressure than in the cylindrical spaces 121, 134a-d so that a total force on the Valve member 134 acts to open it leads. Both the strong spring 125 and also weak spring 126 is compressed. The ones below of the spring plate 126T escapes through the damping openings in the spring seat 126T and therefore slows the opening of the valve member 134.
  • the height of the opening stroke of the valve member 134 and the Amount of fluid delivered to the head of valve member 134 flows into the displacement chamber 129 depends on the pressure p3 in the distribution line 130.
  • valve 150 can be integrated into the pump construction to save space because there are 130a-d does not arrive.
  • the formation of the valve 150 with elongated linear slots 155a-d allow a particularly good one Controllability of the pump down to the smallest delivery rates.
  • poppet valves 134 as intake valves, which here at the same time as the pressure difference actuated according to the invention, throttling 2/2-way valves is in the Rule the cheaper option than using Slider valves, especially the displacement room has one Leakage path less, which is the case with pumps for highest pressures, low speeds and lowest viscosities (as in Connection with the common rail diesel injection) is particularly important if the highest levels of efficiency are achieved should be.
  • the tightness of the intake seat valves 134 also affects the equal promotion of displacement space 129a-d to displacement space 129a-d positive because of leakage in generally has a high component tolerance. Also the General pump characteristics can be found in the Series production in designs with a seat valve is better adhere.
  • Vibrations of the throttling valves can - like general vibrations - to spring breaks or, with seat valves, lead to increased wear or broken shaft, here these vibrations especially damage the Funding characteristic, which is thereby changed. Vibrations often arise randomly as a result of stochastically fluctuating Damping effects or suggestions. In such a case would stochastic flow rate fluctuations at the pump or hysteresis effects occur, both of which use which would complicate pumps for control purposes.
  • valve damping is therefore the use of a Damper proposed on the throttling valve.
  • the damping forces produce with simple piston dampers of known design also negative pressure, which in turn is used for the damping function can create harmful voids.
  • Fig. 7 now shows some for throttle control elements Special features of the design of the throttling valves, for example the valves 30 in Fig. 1 or 150 in the 4 to 6.
  • the pressure difference goes on the adjusting element with the root of the pressure difference in the metered amount of liquid.
  • this pressure difference decreases with increasing Throttle valve opening.
  • the use of a differential pressure valve 40 in Fig. 2 shows how this pressure difference can basically be kept constant by the Use of the differential pressure valve in parallel to the Pressure in front of the throttling valve can also be changed.
  • FIGS. 8 shows the state for the full filling or conveying of the displacer spaces 15, FIG. 9 the state for half the filling or conveying of the displacer spaces 15 and FIG. 10 the state of not exactly zero conveying of the displacer spaces 15 as a function of the angle of rotation of the drive shaft, based on the top dead center OTP and the bottom dead center UTP of the respective displacement pistons 9.
  • the free flow cross section A valve through the inlet valves 28 assumes the maximum value.
  • the valves 28 (FIG. 1) are only partially open.
  • the delivered volumes V correspond to the area under the volume flow functions. 10 shows the case in which the delivery is just O and the filling therefore also tends towards O.
  • the displacers can be filled slightly to cover any piston leakage as a result of the compression / decompression.
  • a minimal opening A suction (V ⁇ O) is therefore shown in FIG. 10.
  • the duration of this opening extends approximately over the entire revolution, interrupted only by the relatively short compression / decompression phase. Similar courses arise for the further embodiments according to FIGS. 2, 3 and 4 to 6 and 13, 14, 15, 16 and 17.
  • Fig. 12 shows the corresponding flow characteristics for slot-controlled pumps, as in the embodiment according to Fig. 2nd
  • Fig. 13 shows an embodiment similar to Fig. 3, however with a different training of the pressure difference actuators throttling 2/2-way valves and with another Type of variable throttle actuation.
  • the 2/2-way valves of the 13 each consist of an embodiment Ball 54, which by means of a spring 53 to a valve seat is pressed.
  • the movement of the ball 54 with respect to the Valve seat in the open state of the valve depends on that pressure prevailing in the respective line 31, 31a and 31b p3, which makes the filling of the displacement spaces dependent is controlled by p3.
  • a converter 27 for 1 particularly for the Integration in analog control loops is suitable switching valve 50 as a converter according to FIG. 13 advantages in connection with digital electronics.
  • FIG. 13 shows such an arrangement, wherein as in Fig. 2 with slot-controlled pumps and at the Opening angle adapted to the number of cylinders, a switching valve 50 for several displacement elements 9 is sufficient.
  • This constellation has advantages if that is to be promoted Fluid is very viscous or contains dirt, which could impair the function (example: Common rail injection system for heavy oil engines), or if the variable pump should be self-priming or only with very low form should be worked. You need then only a much less powerful pressure source 100 for the actuating fluid, often one such a pressure source is already available (e.g. compressed air network).
  • the actuating fluid is connected via lines 101 to the controllable pressure p10 to the individual 2/2-way valves 103 headed.
  • the pressure p10 acts on the Effective area 102 on one side of the slide of the 2/2-way valve 103, while a spring 104 and the output pressure of the 2/2-way valve via line 106 to the effective area 105 acts on the other side of the slide 102.
  • FIG. 15 shows a schematic representation of a pump in a radial design with three displacement pistons 9, only the central part of the pump housing around the drive shaft 12 is shown around and only the upper displacement piston 9 is completely drawn.
  • connection line to the liquid reservoir is as before provided with the reference number 33.
  • Reference numeral 30 indicates an adjustable throttle element, which over the Line 31 leads into the interior 202.
  • the pump of the figure 15 is slot controlled and has inlet slots for this purpose 35 (only shown for the upper displacement piston), the inlet slots 35 each actuated by a pressure difference and throttling 2/2 way valve 51 (as with the Figure 13 shown) and corresponding line sections 204 and 206 in the pump housing communicate with the interior 202.
  • the reference number 17 indicates the outlet valve as before, that via a line 18 with corresponding Lines of the other displacement pistons 9 (not shown) is united and finally to the "Common Rail" the internal combustion engine connected to it.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Rotary Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Steering Control In Accordance With Driving Conditions (AREA)
  • Vehicle Body Suspensions (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)

Claims (18)

  1. Dispositif de commande d'une pompe volumétrique à liquide qui comprend au moins une chambre de refoulement (15 ; 129) qui aspire le liquide à refouler (2) d'un réservoir à liquide (1) ayant une surface libre qui est exposée à la pression d'un gaz (p1), de préférence à la pression atmosphérique, comprenant des moyens réglables (30 ; 60 ; 150 ; 50 ; 34) disposés en amont de la chambre de refoulement (15 ; 129) et destinés à limiter l'afflux dans la chambre de refoulement (15 ; 129) caractérisé par au moins un distributeur étrangleur 2/2 (21 ; 134 ; 51 ; 103) qui est actionné par une différence de pression, qui est couplé en amont à la chambre de refoulement (15 ; 129) et disposé en aval des moyens de limitation de l'afflux (30 ; 60 ; 150 ; 50 ; 34) et qui maintient la pression régnant dans le conduit de raccord (31 ; 41 ; 130 ; 107 ; 31, 202, 204) situé entre les moyens de limitation de l'afflux (30 ; 60 ; 150 ; 50 ; 34) et le distributeur 2/2 (21 ; 134 ; 51 ; 103) à une valeur toujours suffisamment élevée pour que ni de la vapeur, ni du gaz en solution ne soit mêlés au liquide, et toujours supérieure à 0,9 bar absolu.
  2. Dispositif de commande selon la revendication 1, caractérisé en ce qu'une source de pression (8 ; 34) d'alimentation du liquide à une pression suffisamment élevée (P2) est coupléeen amont aux moyens de limitation de l'afflux (30 ; 60 ; 150 ; 50 ;34) et prélève le liquide directement ou indirectement sur le réservoir à liquide (1).
  3. Dispositif de commande selon la revendication 1, caractérisé en ce que l'au moins une chambre de refoulement (15 ; 129) comprend au moins une lumière d'admission (35) ou au moins une soupape d'admission (28) et en ce que l'au moins un distributeur 2/2 (21, 21a, 21b ; 51, 52, 53, 54 ; 103) est disposé très près de la lumière d'admission (35) ou de la soupape d'admission (28).
  4. Dispositif de commande selon la revendication 1, caractérisé en ce que les moyens de limitation de l'afflux comprennent un distributeur étrangleur (30 ; 150) réglable électriquement, mécaniquement, hydrauliquement ou pneumatiquement.
  5. Dispositif de commande selon la revendication 1, caractérisé en ce que les moyens de limitation de l'afflux comprennent une combinaison d'un distributeur étrangleur (30) et d'une soupape (40) commandée par une différence de pression.
  6. Dispositif de commande selon la revendication 1, caractérisé en ce que les moyens de limitation de l'afflux comprennent un distributeur à tout ou rien 2/2 (60) actionné électriquement et modulable par durée d'impulsion.
  7. Dispositif de commande selon la revendication 1, caractérisé en ce qu'au moins un distributeur étrangleur 2/2 (103) comprend un tiroir soumis à la charge d'un ressort et sur une surface efficace duquel (102) agit la pression (p10) d'un fluide provenant d'une source de pression (100) qui fait partie d'un deuxième circuit de fluide.
  8. Dispositif de commande selon la revendication 1, caractérisé en ce que l'au moins un distributeur étrangleur 2/2 est soumis à la charge d'un ressort et est conformé en soupape d'admission (134 ; 51, 52, 53, 54) de l'au moins une chambre de refoulement (15, 129).
  9. Dispositif de commande selon la revendication 1, caractérisé en ce qu'un amortisseur (70) attaque l'au moins un distributeur étrangleur 2/2 (21, 21a, 21b).
  10. Dispositif de commande selon l'une des revendications 1 ou 2, caractérisé en ce que l'au moins un distributeur étrangleur 2/2 (21, 21a, 21b ; 134 ; 51, 52, 53, 54 ; 103) présente une caractéristique d'ouverture raide et en ce que la pression (p2) du liquide dirigé sur les moyens de limitation de l'afflux (30 ; 60; 150 ; 50 ; 34) est suffisamment élevée pour que même pour le flux volumique maximal de la pompe, la différence de pression ne soit pas notablement modifiée par les moyens de limitation de l'afflux (30 ; 60 ; 150 ; 50 ; 34).
  11. Dispositif de commande selon l'une des revendications 1-10, destiné à une pompe volumétrique comprenant plusieurs chambres de refoulement (15, 129), caractérisé en ce qu'au moins un distributeur étrangleur 2/2 (21 ; 134 ; 51 ; 103) est monté en amont des chambres de refoulement (15, 129).
  12. Dispositif de commande selon la revendication 11, caractérisé en ce qu'un distributeur étrangleur 2/2 (21 ; 54 ; 51 ; 103) est monté en amont de chacune des chambres de refoulement (15, 129).
  13. Dispositif de commande selon l'une des revendications 11 ou 12, caractérisé en ce que les moyens de limitation de l'afflux comprennent plusieurs soupapes d'étranglement réglables (30, 30a, 30b, 60, 150) qui sont actionnées en groupes ou toutes ensemble en synchronisme les unes avec les autres.
  14. Dispositif de commande selon la revendication 13, caractérisé par un distributeur à tiroir rotatif (150), dans lequel des soupapes d'étranglement réglables sont réunies et qui comprend une enveloppe (138) comportant plusieurs chambres et dans laquelle un corps de tiroir creux, rotatif ou déplaçable axialement est disposé, des trous (155a-d ; 130a-d) qui sont prévus pour chaque chambre étant disposés deux à deux et se faisant face dans le corps de tiroir et dans l'enveloppe (138).
  15. Dispositif de commande selon la revendication 14, caractérisé en ce que les trous (155a-d ; 130a, 130b, 130c, 130d) qui se font face dans le corps du tiroir et dans l'enveloppe (138) sont réalisés par érosion au moyen d'un fil métallique.
  16. Dispositif de commande selon la revendication 1 pour une pompe volumétrique comprenant un carter comportant un volume interne (202), au moins un piston plongeur (9) et une came excentrique (11) actionnant ce dernier, le volume interne communiquant par des trous correspondants du carter de la pompe et par une lumière d'admission (35) avec d'au moins une chambre de refoulement, caractérisé en ce qu'au moins un distributeur étrangleur 2/2 (51) est disposé soit dans le carter de la pompe, au-devant de la lumière d'admission (35), soit dans au moins un piston plongeur (9).
  17. Dispositif de commande selon la revendication 16, destiné à une pompe volumétrique comprenant plusieurs chambres de refoulement et un nombre correspondant de pistons plongeurs (9), chaque chambre de refoulement communiquant par une lumière d'admission (35) avec le volume interne (202), caractérisé en ce que les moyens de limitation de l'afflux (30) sont communs à toutes les chambres de refoulement et sont disposés dans un conduit (33, 31) situé entre le réservoir de liquide (1) et le volume interne (202).
  18. Dispositif de commande selon la revendication 1, destiné à une pompe volumétrique comprenant plusieurs chambres de refoulement et un nombre correspondant de pistons plongeurs (9), chaque chambre de refoulement comprenant une lumière (35) d'admission du liquide à refouler, caractérisé en ce que les lumières d'admission (35) et les pistons plongeurs (9) coopérant avec celles-ci sont conçus de manière que la phase d'ouverture des lumières d'admission (35) soit d'environ 360° divisés par le nombre des pistons plongeurs (9), de préférence d'un peu moins, de manière que la limitation de l'afflux soit possible au moyen d'un unique élément (30) de limitation de l'afflux.
EP94930902A 1993-11-08 1994-11-07 Dispositif de commande pour une pompe a volume de remplissage variable Expired - Lifetime EP0678166B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CH3367/93 1993-11-08
CH336793 1993-11-08
PCT/CH1994/000215 WO1995013474A1 (fr) 1993-11-08 1994-11-07 Dispositif de commande pour une pompe a volume de remplissage variable
CA002151518A CA2151518A1 (fr) 1993-11-08 1995-06-07 Dispositif de regulation pour pompe a debit variable

Publications (2)

Publication Number Publication Date
EP0678166A1 EP0678166A1 (fr) 1995-10-25
EP0678166B1 true EP0678166B1 (fr) 1998-08-12

Family

ID=25678018

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94930902A Expired - Lifetime EP0678166B1 (fr) 1993-11-08 1994-11-07 Dispositif de commande pour une pompe a volume de remplissage variable

Country Status (9)

Country Link
US (1) US5701873A (fr)
EP (1) EP0678166B1 (fr)
JP (1) JP3747061B2 (fr)
CN (1) CN1082143C (fr)
AT (1) ATE169720T1 (fr)
CA (1) CA2151518A1 (fr)
DE (1) DE59406680D1 (fr)
ES (1) ES2120076T3 (fr)
WO (1) WO1995013474A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2798961A1 (fr) * 1999-09-29 2001-03-30 Bosch Gmbh Robert Systeme d'injection de carburant a pompe a haute pression
DE102007060262A1 (de) 2007-12-14 2009-06-18 Robert Bosch Gmbh Pumpenanordnung und Verfahren zu deren Ansteuerung

Families Citing this family (59)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0902181B1 (fr) * 1997-09-11 2003-12-17 Denso Corporation Pompe à haute pression à débit variable
JP3999855B2 (ja) * 1997-09-25 2007-10-31 三菱電機株式会社 燃料供給装置
DE19818421B4 (de) 1998-04-24 2017-04-06 Robert Bosch Gmbh Kraftstoffversorgungsanlage einer Brennkraftmaschine
EP1000245B1 (fr) * 1998-05-26 2004-08-25 Caterpillar Inc. Systeme hydraulique avec pompe a debit variable
DE19846157A1 (de) * 1998-10-07 2000-04-13 Bosch Gmbh Robert Pumpenanordnung zur Kraftstoffhochdruckerzeugung
DE19846940B4 (de) * 1998-10-12 2007-09-06 Hydraulik-Ring Gmbh Pumpenanordnung
JP2000130279A (ja) * 1998-10-21 2000-05-09 Toyota Motor Corp 内燃機関の高圧燃料供給装置
DE19853103A1 (de) * 1998-11-18 2000-05-25 Bosch Gmbh Robert Kraftstoffeinspritzsystem für Brennkraftmaschinen
JP4088738B2 (ja) 1998-12-25 2008-05-21 株式会社デンソー 燃料噴射ポンプ
DE19902259B4 (de) * 1999-01-21 2006-02-23 Siemens Ag Montageverfahren
DE19904341A1 (de) * 1999-02-03 2000-08-10 Mannesmann Rexroth Ag Steuerungsverfahren
DE19907311A1 (de) 1999-02-22 2000-08-31 Bosch Gmbh Robert Hydraulikpumpeneinheit
DE19909329A1 (de) * 1999-03-03 2000-09-07 Mannesmann Rexroth Ag Kraftstoffeinspritzsystem
JP2000310171A (ja) * 1999-04-27 2000-11-07 Mitsubishi Electric Corp 燃料供給装置
DE19927826A1 (de) * 1999-06-18 2000-12-28 Bosch Gmbh Robert Pumpenanordnung
DE19938751A1 (de) * 1999-08-16 2001-03-01 Siemens Ag Einspritzanlage für eine Brennkraftmaschine, insbesondere für eine Common-Rail-Einspritzanlage
DE19941850B4 (de) * 1999-09-02 2005-03-31 Siemens Ag Einspritzanlage für eine Brennkraftmaschine
DE19959006C1 (de) * 1999-12-08 2000-12-21 Bosch Gmbh Robert Radialkolbenpumpe
DE10005212A1 (de) * 2000-02-05 2001-09-27 Bosch Gmbh Robert Verfahren und Einrichtung zum Ansteuern eines elektromagnetischen Mengensteuerventils
DE10115324A1 (de) * 2001-03-28 2002-10-17 Bosch Gmbh Robert Kraftstoffsystem
DE10139054C1 (de) * 2001-08-08 2003-01-30 Bosch Gmbh Robert Verfahren, Computerprogramm, Steuer- und/oder Regelgerät sowie Kraftstoffsystem für eine Brennkraftmaschine, insbesondere mit Direkteinspritzung
DE10153185A1 (de) * 2001-10-27 2003-05-15 Bosch Gmbh Robert Kraftstoffeinspritzanlage mit verbesserter Fördermengenregelung
ITTO20011039A1 (it) * 2001-10-30 2003-04-30 Ct Studi Componenti Per Veicol Valvola di aspirazione per una pompa ad alta pressione, in particolare per combustibile di un motore endotermico.
EP1321663A3 (fr) * 2001-12-19 2003-07-02 Robert Bosch Gmbh Dispositif d'injection de combustible pour moteur à combustion interne
DE10205187A1 (de) * 2002-02-08 2003-08-21 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
EP1617073B1 (fr) * 2003-04-24 2008-12-10 Bosch Corporation Procede de regulation du debit dans un injecteur de carburant dans un accumulateur et injecteur de carburant dans un accumulateur
JP3894179B2 (ja) 2003-10-02 2007-03-14 トヨタ自動車株式会社 内燃機関の燃料供給装置
WO2005052357A1 (fr) * 2003-11-28 2005-06-09 Ganser-Hydromag Ag Pompe d'alimentation haute pression destinee a des moteurs a combustion interne
DE102005033638A1 (de) * 2005-07-19 2007-01-25 Robert Bosch Gmbh Kraftstoff-Fördereinrichtung, insbesondere für eine Brennkraftmaschine
DE102005051482A1 (de) * 2005-10-27 2007-05-03 Brueninghaus Hydromatik Gmbh Lastdruckgeführter Förderstromregler mit Schwingungsdämpfung
FI118055B (fi) * 2005-11-23 2007-06-15 Waertsilae Finland Oy Mäntämoottorin ruiskutuspumppu
US7857605B2 (en) * 2006-06-29 2010-12-28 Caterpillar Inc Inlet throttle controlled liquid pump with cavitation damage avoidance feature
WO2008030760A2 (fr) 2006-09-05 2008-03-13 New York Air Brake Corporation Système de compresseur d'air sans huile à régulateur d'admission
JP4672637B2 (ja) * 2006-11-02 2011-04-20 三菱重工業株式会社 エンジンの燃料噴射装置
SE530565C2 (sv) * 2006-11-10 2008-07-08 Scania Cv Ab Bränslepumpanordning
US7444989B2 (en) 2006-11-27 2008-11-04 Caterpillar Inc. Opposed pumping load high pressure common rail fuel pump
FR2914959B1 (fr) * 2007-04-13 2013-03-08 Siemens Automotive Hydraulics Sa Perfectionnement aux dispositifs d'alimentation de carburant sous haute pression par pompe transfert
DE102008040083A1 (de) * 2008-07-02 2010-01-07 Robert Bosch Gmbh Hochdruckpumpe
DE102009003066A1 (de) * 2009-05-13 2010-11-18 Robert Bosch Gmbh Kolbenmaschine, insbesondere Flüssigkeitskolbenmaschine
JP5825693B2 (ja) * 2010-07-14 2015-12-02 ボルボ ラストバグナー アーベー 圧力コントロールされるブリード機能を伴う燃料噴射システム
DE112011105591B4 (de) * 2011-09-06 2017-03-16 Toyota Jidosha Kabushiki Kaisha Kraftstoffpumpe und Kraftstofffördersystem für Maschine mit interner Verbrennung
US8926298B2 (en) 2012-01-04 2015-01-06 Husco International, Inc. Hydraulic piston pump with a variable displacement throttle mechanism
US9062665B2 (en) * 2013-01-15 2015-06-23 Husco International, Inc. Hydraulic piston pump with throttle control
JP6111116B2 (ja) * 2013-03-28 2017-04-05 Ｋｙｂ株式会社 ポンプ容積制御装置
DE102014219488A1 (de) 2014-09-25 2016-03-31 Mahle International Gmbh Pumpvorrichtung, insbesondere Axialkolbenpumpe, für eine Abwärmenutzungseinrichtung eines Kraftfahrzeugs
DE102014219487A1 (de) * 2014-09-25 2016-03-31 Mahle International Gmbh Pumpvorrichtung, insbesondere Axialkolbenpumpe, für eine Abwärmenutzungseinrichtung eines Kraftfahrzeugs
NL2014285B1 (nl) * 2015-02-12 2016-10-13 Rio Boxx Holding B V Pompsysteem.
GB201502686D0 (en) * 2015-02-18 2015-04-01 Finishing Brands Uk Ltd High pressure pump
JP6432440B2 (ja) * 2015-05-15 2018-12-05 株式会社デンソー 高圧ポンプ
GB2554005A (en) 2015-07-10 2018-03-21 Husco Int Inc Radial piston pump assemblies and use thereof in hydraulic circuits
US10975816B2 (en) * 2017-11-27 2021-04-13 Stanadyne Llc Roller drive mechanism for GDI pump
IT201800003340A1 (it) * 2018-03-07 2019-09-07 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna
DE102018001913A1 (de) * 2018-03-08 2019-09-12 Woodward L'orange Gmbh Anordnung mit einer Hochdruckpumpe und einer dieser vorgeordneten Regeleinrichtungen
CH715387A1 (de) 2018-09-27 2020-03-31 Ganser Hydromag Common Rail für eine Brennstoffeinspritzvorrichtung.
CN114341492A (zh) * 2019-06-11 2022-04-12 克洛布股份公司 用于分配流体产品的组件、设备和方法
IT201900015099A1 (it) * 2019-08-27 2021-02-27 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna
GB2589717B (en) * 2019-09-18 2023-12-20 7Rdd Ltd Pressure washer apparatus
CH716632A1 (de) * 2019-09-25 2021-03-31 Liebherr Machines Bulle Sa Reihenkolbenpumpe.
CN111396384B (zh) * 2020-04-08 2022-05-13 重庆凯瑞汽车试验设备开发有限公司 一种用于拉杆式静压油缸的插装式节流器阀组

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE680810C (de) * 1936-02-18 1939-09-07 Teves Kg Alfred Kolbenpumpe
US2653543A (en) * 1950-05-03 1953-09-29 Hobson Ltd H M Hydraulic pump
CH346728A (fr) * 1956-11-20 1960-05-31 Etienne Bessiere Pierre Pompe à piston à autorégulation de débit
NO142139C (no) * 1976-05-31 1980-07-02 Akers Mek Verksted As Fremgangsmaate for regulering av leveringsmengden for en stempelpumpe, samt en anordning for utfoerelse av samme
US4406264A (en) * 1980-07-26 1983-09-27 Lucas Industries Limited Governor for engines
FR2508112B1 (fr) * 1981-06-19 1986-05-02 Citroen Sa Regulateur de pompe par etranglement a l'aspiration avec limiteur de pression incorpore
US4474158A (en) * 1981-11-11 1984-10-02 Lucas Industries Public Limited Company Liquid fuel pumping apparatus
GB2109058B (en) * 1981-11-11 1985-02-20 Lucas Ind Plc Liquid fuel pumping apparatus
EP0111200B1 (fr) * 1982-11-25 1988-02-03 Kawasaki Jukogyo Kabushiki Kaisha Système de contrôle d'avance pour l'injection de carburant
GB2131493B (en) * 1982-12-08 1985-11-13 Lucas Ind Plc Fuel injection pumping apparatus
DE3440942A1 (de) * 1984-11-09 1986-05-15 Robert Bosch Gmbh, 7000 Stuttgart Piezoelektrischer steuerblock
US4907949A (en) * 1986-12-16 1990-03-13 Regie Nationale Des Usines Renault Variable flow pump
DE3714691A1 (de) * 1987-05-02 1988-12-01 Backe Wolfgang Mehrwegeventil
CH674243A5 (fr) * 1987-07-08 1990-05-15 Dereco Dieselmotoren Forschung
DE3885689T2 (de) * 1987-09-16 1994-03-24 Nippon Denso Co Hochdruckverstellpumpe.
US5156531A (en) * 1988-09-15 1992-10-20 Zahnradfabrik Friedrichshafen, Ag. Radial piston pump
US5197441A (en) * 1989-06-03 1993-03-30 Lucas Industries Fuel injection pumping apparatus
JP2829639B2 (ja) * 1989-09-22 1998-11-25 株式会社ゼクセル 電子制御式分配型燃料噴射ポンプの送油率可変制御方法
DE3937709A1 (de) * 1989-11-13 1991-05-16 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US5167493A (en) * 1990-11-22 1992-12-01 Nissan Motor Co., Ltd. Positive-displacement type pump system
US5479899A (en) * 1994-10-13 1996-01-02 Phelps Fuel Systems, Inc. Fuel management system

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2798961A1 (fr) * 1999-09-29 2001-03-30 Bosch Gmbh Robert Systeme d'injection de carburant a pompe a haute pression
DE19946610A1 (de) * 1999-09-29 2001-04-12 Bosch Gmbh Robert Kraftstoffeinspritzsystem und Kraftstoffhochdruckpumpe
DE19946610B4 (de) * 1999-09-29 2009-09-10 Robert Bosch Gmbh Kraftstoffeinspritzsystem und Kraftstoffhochdruckpumpe
DE102007060262A1 (de) 2007-12-14 2009-06-18 Robert Bosch Gmbh Pumpenanordnung und Verfahren zu deren Ansteuerung

Also Published As

Publication number Publication date
JP3747061B2 (ja) 2006-02-22
JPH08505680A (ja) 1996-06-18
US5701873A (en) 1997-12-30
WO1995013474A1 (fr) 1995-05-18
CN1116441A (zh) 1996-02-07
EP0678166A1 (fr) 1995-10-25
ATE169720T1 (de) 1998-08-15
CN1082143C (zh) 2002-04-03
CA2151518A1 (fr) 1996-12-08
ES2120076T3 (es) 1998-10-16
DE59406680D1 (de) 1998-09-17

Similar Documents

Publication Publication Date Title
EP0678166B1 (fr) Dispositif de commande pour une pompe a volume de remplissage variable
DE69027858T2 (de) Hydraulisches stellglied
DE19917506B4 (de) Verstellbare Flügelzellenpumpe
DE2503346C2 (de) Kraftstoffverteilereinspritzpumpe für Brennkraftmaschinen
EP0328602B1 (fr) Dispositif d'introduction de carburant dans la chambre de combustion d'un moteur a combustion interne
DE1070442B (de) Brennstoff-Einspritzsystem fur Brennkraftmaschinen
DE69302047T2 (de) Hubventilsteuerungsvorrichtung einer Brennkraftmaschine
DE2638736A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE60301312T2 (de) Treibstoffpumpenanordnung
EP0070558B1 (fr) Pompe d'injection de carburant
DE1947529C3 (de) Kraftstoff einspritzpumpe für Brennkraftmaschinen
DE4118555A1 (de) Foerderbeginnverstelleinrichtung einer kraftstoffeinspritzpumpe
EP0509077B1 (fr) Pompe a pistons, notamment pompe a pistons radiaux
EP1247978B1 (fr) Système d'injection de carburant pour un moteur à combustion interne
DE2918867C2 (de) Kraftstoffeinspritzpumpe für Brennkraftmaschinen mit einer Steuereinrichtung für die Änderung des Förderbeginns
EP3406866A1 (fr) Entraînement hydraulique destiné à accélérer ou ralentir dynamiquement des composants en mouvement
EP1269021B1 (fr) Pompe a pistons radiaux
EP1049869B1 (fr) Dispositif pour produire un debit variable dans une alimentation en carburant
DE4311672A1 (de) Kraftstoffeinspritzpumpe
DE1805276B2 (de) Regeleinrichtung an einer brennstoffeinspritzpumpe fuer brennkraftmaschinen
DE1776071C3 (de) Kraftstoffeinspritzanlage für Brennkraftmaschinen mit einem Hydraulikstellglied zur Verstellung des Einspritzzeitpunktes
WO2014127905A1 (fr) Compresseur à piston
DE3804778C2 (fr)
DE19712557B4 (de) Verteiler-Kraftstoffeinspritzpumpe für einen Verbrennungsmotor mit innerer Verbrennung
DE3832137C2 (fr)

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19950616

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE ES FR GB IE IT LI NL SE

17Q First examination report despatched

Effective date: 19960306

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SIG SCHWEIZERISCHE INDUSTRIE-GESELLSCHAFT

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE ES FR GB IE IT LI NL SE

REF Corresponds to:

Ref document number: 169720

Country of ref document: AT

Date of ref document: 19980815

Kind code of ref document: T

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: PATENTANWAELTE SCHAAD, BALASS, MENZL & PARTNER AG

Ref country code: CH

Ref legal event code: EP

ITF It: translation for a ep patent filed

Owner name: GUZZI E RAVIZZA S.R.L.

REF Corresponds to:

Ref document number: 59406680

Country of ref document: DE

Date of ref document: 19980917

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19980911

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2120076

Country of ref document: ES

Kind code of ref document: T3

ET Fr: translation filed
REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: GERMAN

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

PLBF Reply of patent proprietor to notice(s) of opposition

Free format text: ORIGINAL CODE: EPIDOS OBSO

26 Opposition filed

Opponent name: SIEMENS AG ZENTRALABTEILUNG TECHNIK ZT PA5

Effective date: 19990512

PLBF Reply of patent proprietor to notice(s) of opposition

Free format text: ORIGINAL CODE: EPIDOS OBSO

PLBO Opposition rejected

Free format text: ORIGINAL CODE: EPIDOS REJO

REG Reference to a national code

Ref country code: CH

Ref legal event code: PUE

Owner name: SIG SCHWEIZERISCHE INDUSTRIE-GESELLSCHAFT -DANN AN

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: CRT COMMON RAIL TECHNOLOGIES AG

RTI2 Title (correction)

Free format text: CONTROL DEVICE FOR A VARIABLE INTAKE VOLUME PUMP

APAC Appeal dossier modified

Free format text: ORIGINAL CODE: EPIDOS NOAPO

APAE Appeal reference modified

Free format text: ORIGINAL CODE: EPIDOS REFNO

NLT2 Nl: modifications (of names), taken from the european patent patent bulletin

Owner name: CRT COMMON RAIL TECHNOLOGIES AG

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

NLS Nl: assignments of ep-patents

Owner name: CRT COMMON RAIL TECHNOLOGIES AG

REG Reference to a national code

Ref country code: FR

Ref legal event code: TP

APAC Appeal dossier modified

Free format text: ORIGINAL CODE: EPIDOS NOAPO

PLBN Opposition rejected

Free format text: ORIGINAL CODE: 0009273

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: OPPOSITION REJECTED

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

27O Opposition rejected

Effective date: 20011215

NLR2 Nl: decision of opposition
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IE

Payment date: 20021023

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20021028

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 20021029

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20021114

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20031107

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20031108

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20031130

BERE Be: lapsed

Owner name: *CRT COMMON RAIL TECHNOLOGIES A.G.

Effective date: 20031130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040601

EUG Se: european patent has lapsed
NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 20040601

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

APAH Appeal reference modified

Free format text: ORIGINAL CODE: EPIDOSCREFNO

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: RENTSCH & PARTNER

REG Reference to a national code

Ref country code: CH

Ref legal event code: PFA

Owner name: CRT COMMON RAIL TECHNOLOGIES AG

Free format text: CRT COMMON RAIL TECHNOLOGIES AG#INDUSTRIEPLATZ 1#8212 NEUHAUSEN AM RHEINFALL (CH) -TRANSFER TO- CRT COMMON RAIL TECHNOLOGIES AG#INDUSTRIEPLATZ 1#8212 NEUHAUSEN AM RHEINFALL (CH)

REG Reference to a national code

Ref country code: CH

Ref legal event code: PLI

Owner name: LIEBHERR MACHINES BULLE SA

Free format text: MALI COMMON RAIL TECHNOLOGIES AG#ANTHOPTSTRASSE 9#8222 BERINGEN (CH) -TRANSFER TO- LIEBHERR MACHINES BULLE SA#RUE DE L'INDUSTRIE 45#1630 BULLE (CH)

Ref country code: CH

Ref legal event code: PFA

Owner name: MALI COMMON RAIL TECHNOLOGIES AG

Free format text: CRT COMMON RAIL TECHNOLOGIES AG#INDUSTRIEPLATZ 1#8212 NEUHAUSEN AM RHEINFALL (CH) -TRANSFER TO- MALI COMMON RAIL TECHNOLOGIES AG#ANTHOPTSTRASSE 9#8222 BERINGEN (CH)

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20131121

Year of fee payment: 20

Ref country code: AT

Payment date: 20131113

Year of fee payment: 20

Ref country code: CH

Payment date: 20131121

Year of fee payment: 20

Ref country code: GB

Payment date: 20131120

Year of fee payment: 20

Ref country code: FR

Payment date: 20131120

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20131128

Year of fee payment: 20

Ref country code: IT

Payment date: 20131128

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 59406680

Country of ref document: DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 59406680

Country of ref document: DE

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Expiry date: 20141106

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK07

Ref document number: 169720

Country of ref document: AT

Kind code of ref document: T

Effective date: 20141107

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20141106

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20150826

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20141108

REG Reference to a national code

Ref country code: DE

Ref legal event code: R039

Ref document number: 59406680

Country of ref document: DE

Ref country code: DE

Ref legal event code: R008

Ref document number: 59406680

Country of ref document: DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 59406680

Country of ref document: DE

Representative=s name: G&P RECHTSANWALTSGESELLSCHAFT MBH, DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 59406680

Country of ref document: DE

Representative=s name: G&P RECHTSANWALTSGESELLSCHAFT MBH, DE

Ref country code: DE

Ref legal event code: R081

Ref document number: 59406680

Country of ref document: DE

Owner name: MALI COMMON RAIL TECHNOLOGIES AG, CH

Free format text: FORMER OWNER: CRT COMMON RAIL TECHNOLOGIES AG, NEUHAUSEN, CH

REG Reference to a national code

Ref country code: DE

Ref legal event code: R040

Ref document number: 59406680

Country of ref document: DE