EP2495431B1 - Hydraulikpumpe, insbesondere eine Kraftstoffpumpe - Google Patents

Hydraulikpumpe, insbesondere eine Kraftstoffpumpe Download PDF

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Publication number
EP2495431B1
EP2495431B1 EP20110157051 EP11157051A EP2495431B1 EP 2495431 B1 EP2495431 B1 EP 2495431B1 EP 20110157051 EP20110157051 EP 20110157051 EP 11157051 A EP11157051 A EP 11157051A EP 2495431 B1 EP2495431 B1 EP 2495431B1
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EP
European Patent Office
Prior art keywords
delivery
pressure
pump
hydraulic
valve
Prior art date
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Application number
EP20110157051
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English (en)
French (fr)
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EP2495431A1 (de
Inventor
Claudio Negri
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OMT Officine Meccaniche Torino SpA
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OMT Officine Meccaniche Torino SpA
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Publication date
Application filed by OMT Officine Meccaniche Torino SpA filed Critical OMT Officine Meccaniche Torino SpA
Priority to DK11157051T priority Critical patent/DK2495431T3/da
Priority to EP20110157051 priority patent/EP2495431B1/de
Priority to JP2012035345A priority patent/JP5866225B2/ja
Priority to KR1020120021829A priority patent/KR101540502B1/ko
Priority to CN201210052526.5A priority patent/CN102654091B/zh
Publication of EP2495431A1 publication Critical patent/EP2495431A1/de
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Publication of EP2495431B1 publication Critical patent/EP2495431B1/de
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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
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/462—Delivery valves
    • 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
    • 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
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0028—Valves characterised by the valve actuating means hydraulic
    • F02M63/0029—Valves characterised by the valve actuating means hydraulic using a pilot valve controlling a hydraulic chamber
    • 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
    • F04B49/08—Regulating by delivery pressure
    • 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
    • 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
    • F04B49/24—Bypassing
    • F04B49/246—Bypassing by keeping open the outlet valve
    • 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
    • F04B2201/00—Pump parameters
    • F04B2201/06—Valve parameters
    • F04B2201/0601—Opening times
    • F04B2201/06012—Opening times of the outlet valve only
    • 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
    • F04B2205/05—Pressure after the pump outlet
    • 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

Definitions

  • the present invention relates to a hydraulic pump, in particular a fuel pump.
  • fuel pumps are known, for example, from DE-A-10327411 , EPA-1707801 and EP-A-0163078 .
  • the invention has been developed with reference to hydraulic pumps with devices for regulating the flowrate.
  • the first way of regulation is energetically very expensive in so far as the lamination of fluid that is obtained entails high energy losses.
  • the second way of regulation presents big problems of wear linked to the cavitation induced in the fluid at the pump inlet. Furthermore, said solution normally requires the use of a lamination valve of an electroactuated type with a costly proportional solenoid to be able to vary with continuity and precision the flowrate of fluid that is sucked in by the pump.
  • the object of the present invention is to overcome the technical problems described previously.
  • the object of the invention is to regulate the flowrate delivered by a hydraulic pump to a user in an energetically convenient way and so as not to jeopardize the service life of the pump and of the components thereof.
  • the reference HP designates a hydraulic pump according to various embodiments of the present invention.
  • the pump HP comprises an intake port IP, a delivery port DP, and at least one cylinder CY, set within which is a piston P that moves with reciprocating motion by means of a mechanism K (for example, a cam or a crank mechanism), which is in turn actuated by means of an input shaft IS.
  • a mechanism K for example, a cam or a crank mechanism
  • Each piston P moves with reciprocating motion between a top dead centre TDC and a bottom dead centre BDC.
  • the intake port IP is arranged for connection to an intake environment (not illustrated) and is in fluid communication with the cylinder CY by means of a intake valve IV, in itself known.
  • the cylinder CY is moreover in fluid communication with the delivery port DP by means of a delivery line DL, set on which is a delivery valve DV that can be controlled by means of a regulation assembly R.
  • the delivery valve DV is movable between an open position, where it is arranged for enabling a flow of fluid between the cylinder CY and the delivery port DP, and a closed position, where it prevents the aforesaid flow of fluid between the cylinder CY and the delivery port DP.
  • the pump HP is moreover arranged for hydraulic connection to a user, here represented schematically and designated by the letter U.
  • the user U can be a fuel-accumulation injection system commonly known as "common-rail injection system ".
  • the piston P in reciprocating motion between the top dead centre TDC and the bottom dead centre BDC describes a working cycle comprising a sequence of five phases, namely,
  • the compression and delivery phases develop substantially during the rise of the piston from the bottom dead centre BDC to the top dead centre TDC
  • the reflux, expansion, and intake phases develop substantially during descent of the piston from the top dead centre TDC to the bottom dead centre BDC.
  • the former will be referred to briefly as “rising phase”, and the latter as “descent phase”.
  • the regulation assembly is arranged for receiving a first driving signal PS1, preferentially corresponding to a delivery pressure immediately downstream of the cylinder CY and issuing, as a function of said driving signal PS1, an actuation signal AS1 to the delivery valve DV, for example an actuation force developed with mechanical actuators or with hydraulic means.
  • the actuation force developed on the valve DV causes the opening thereof, thereby enabling the passage of fluid through the delivery line DL and the delivery thereof to the user U through the delivery port DP.
  • the regulation assembly R ceases issuing the actuation signal AS1, enabling closing of the delivery valve DV.
  • the regulation assembly R is arranged for receiving a second driving signal PS2 corresponding to a pressure of the fluid in the user U.
  • the regulation assembly R continues to issue the actuation signal AS1 for keeping the actuation force on the delivery valve DV, and in turn keeping the delivery valve DV in the open position even after the end of the delivery phase.
  • the regulation assembly R keeps the delivery valve open also during at least part of the descent phase of the piston P.
  • the reflux phase performed by the piston P which in conditions of operation at full flowrate is substantially an undesirable effect due to the inertia of the system (delivery valve above all), becomes in conditions of regulation an effect that is sought and develops over a much wider angular range (with reference to an angle of rotation of the input shaft IS) that extends, in the limit, as far as the bottom dead centre BDC (there is thus witnessed a substantial dilation of the reflux phase, with delay and substantial contraction of the intake phase).
  • the regulation assembly R is thus arranged for ceasing the maintenance of the actuation signal AS1 on the delivery valve DV when the pressure of the fluid in the user U drops below the threshold pressure p REF , so that the valve DV is able to reclose.
  • the operation of the regulation assembly R is such that, in conditions of regulation, the pressure of the fluid in the user U oscillates with respect to the reference value, with reiteration of the regulation process just described. In this way, it is possible to guarantee continuously that a flow-rate value equal to the one required reaches the user U.
  • the pump HP comprises an actuator A1, arranged for the actuation of the delivery valve DV, and an elastic positioning element S, whose action tends to bring the delivery valve DV into the closed position.
  • the operation is similar to what has been described previously because the regulation assembly R is arranged for controlling the actuator A1 so as to bring the delivery valve DV into the open position during the delivery phase (as a function of the driving signal PS1) and so as to keep it open during the reflux phase as a function of the driving signal PS2, i.e., of the pressure in the user U.
  • the reference number 1 designates as a whole a hydraulic pump according to a preferred embodiment of the present invention.
  • the schematic representation with a dashed and double-dotted line indicates a body of the hydraulic pump 1.
  • the hydraulic pump 1 comprises an intake port 2 and a delivery port 4.
  • a first manifold channel 6 is in hydraulic communication with the intake port 2, and branching off therefrom, in this embodiment, are a first intake line 8, a second intake line 10, and a third intake line 12 in hydraulic communication with the manifold 6.
  • the intake valves 14, 16, 18 are arranged for enabling or disabling a hydraulic connection between the corresponding intake lines 14, 16, 18 and a first cylinder 20, a second cylinder 22, and a third cylinder 24, respectively.
  • Movable respectively within the cylinders 20, 22, 24 are a first piston P1, a second piston P2, and a third piston P3.
  • Each of the pistons P1, P2, P3 is actuated with reciprocating motion by means of a mechanism.
  • cams C1, C2, C3 (with corresponding tappets) have been provided, uniformly offset in an angular direction.
  • the embodiment of the pump 1 described herein is, by way of example, of the three-piston type, but the person skilled in the art will appreciate that the present invention applies irrespective of the number of the pistons of the pump 1, which can be different from three, even just one.
  • each of the cylinders 20, 22, 24 is in hydraulic communication, respectively, with a first delivery valve 26, a second delivery valve 28, and a third delivery valve 30, which are each movable between a closed position and an open position.
  • Each delivery valve 26, 28, 30 is hydraulically connected, by means of a respective delivery channel 32, 34, 36, to a second manifold channel 38, which is in turn hydraulically connected to the delivery port 4.
  • Each delivery valve 26, 28, 30 is normally in a closed position and is designed to enable, in the open position, a hydraulic connection of the corresponding cylinder 20, 22, 24 associated thereto with the corresponding delivery channel 32, 34, 36 and hence enable a flow of fluid from the corresponding cylinder 20, 22, 24 to the delivery port 4. In a closed position each delivery valve prevents the aforesaid flow of fluid.
  • Each of the delivery valves 26, 28, 30 is controlled by means of a number of actuation signals, which result in corresponding actuation forces.
  • said actuation forces are obtained by hydraulic driving lines, or, more briefly, driving lines.
  • each delivery valve 26, 28, 30 is controlled, respectively, by:
  • Each delivery valve 26, 28, 30 moreover comprises a respective elastic element S1, S2, S3, the action of which is aimed at keeping the corresponding delivery valve in a closed position.
  • the force developed by each elastic element S1, S2, S3 is chosen in such a way as to be substantially negligible with respect to the forces developed by the hydraulic driving lines.
  • hydraulic driving line or “driving line” are used to indicate synthetically a hydraulic line with driving function, i.e., a hydraulic line that in general is able to process a negligible flowrate of fluid and in which the pressure of the fluid within it is exploited as signal of a hydraulic type within a component or a circuit.
  • the first and second driving lines U1, U2, U3 and D1, D2, D3 act on respective surfaces of influence of the corresponding delivery valves 26, 28, 30 to cause opening thereof.
  • the hydraulic driving lines CV1, CV2, CV3, like the elastic elements S1, S2, S3 develop an action aimed at keeping the corresponding delivery valves in the closed position.
  • each hydraulic driving line CV1, CV2, CV3 acts on a respective influence area chosen preferentially in such a way that it is substantially equal to the sum of the influence areas on which the remaining hydraulic driving lines of the corresponding delivery valve act, i.e., the driving lines U1, U2, U3 and D1, D2, D3 (if present).
  • the hydraulic driving lines CV1, CV2, CV3 branch off from a control channel CV0 hydraulically connected to a control volume CV.
  • the control volume CV is hydraulically connected to the second manifold channel 38 and to the delivery port 4 by means of a hydraulic control line 39, set on which is a choke 40, preferentially with fixed geometry.
  • the choke 40 is set hydraulically upstream of the control volume CV.
  • the control volume CV is moreover hydraulically connected to the first manifold channel 6 and to the intake port 2 by means of a control valve 42 set fluid-dynamically downstream thereof in a return channel 43 hydraulically connected to the intake port 2.
  • the control valve 42 is functionally a pressure-regulating valve, which in this embodiment is kept in a closed position by means of an elastic element S4. Furthermore, in this embodiment the control valve 42 can be actuated by means of a solenoid 44 operatively connected to an electronic control unit 46.
  • a regulation assembly of the pump 1 comprising in this embodiment the hydraulic control line 39, the choke 40, the control volume CV, and the control valve 42 (and, in this embodiment, also the control unit 46), which enables, as will emerge clearly from the ensuing description, a variation in the flowrate sent by the pump 1 to a user that is connected to the delivery port 4.
  • the intake port 2 is hydraulically connected to a low-pressure environment LPE that is located fluid-dynamically upstream thereof.
  • the low-pressure environment LPE comprises, for example, a hydraulic inflow line, in which the fuel is moderately pressurized by means of a low-pressure pump that sucks in fuel directly from a tank.
  • the delivery port 4 is instead hydraulically connected to a fuel accumulator, commonly referred to as "common rail” (represented schematically and designated by the reference CR), to which one or more fuel injectors (not illustrated) are hydraulically connected.
  • common rail represented schematically and designated by the reference CR
  • injectors not illustrated
  • the input shaft IS is driven in rotation and actuates each of the pistons P1, P2, P3 with reciprocating motion thanks to the respective cams C1, C2, C3.
  • Each piston P1, P2, P3 describes a working cycle comprising five phases, in a way identical to what was described previously for the piston P.
  • Each piston P1, P2, P3 varies, with its reciprocating motion, the volume of the fluid chamber defined with the corresponding cylinder 20, 22, 24 and is movable between a top dead centre TDC and a bottom dead centre BDC.
  • the angular range of observation has been chosen in such a way as to have an origin coinciding with the top dead centre TDC of the piston P1 and in such a way as to cover a number of work cycles sufficient for describing a transition from a full-flowrate operating condition to a operating condition in a flowrate-regulation regime.
  • the piston P1 is in a position corresponding to the top dead centre TDC, where the reflux phase starts, which in these conditions is due to the inertia of the delivery valve that causes delayed closing thereof with respect to the top dead centre TDC.
  • the expansion phase during which the piston P1 descends to the bottom dead centre BDC, causing a pressure drop within the cylinder 20.
  • the intake valve 14 opens, with consequent entry of fluid into the cylinder 20 from the low-pressure environment LPE through the first manifold channel 6 and the first intake channel 8.
  • the intake phase terminates substantially when the piston P1 reaches the bottom dead centre BDC. At this point the intake valve 14 closes, isolating the volume 20 from the low-pressure line 8, after which rising of the piston to the top dead centre TDC causes the pressurization (compression phase) of the fluid within the cylinder 20. It should be noted, with reference to Figure 6 , that the flowrate through the delivery valve 26 is zero during the compression phase.
  • the pressurization of the fluid in the cylinder 20 causes the opening of the delivery valve 26, with the modalities described in what follows (the delivery phase starts).
  • the delivery valve 26 is subject to the action of the first driving line U1 and of the second driving line CV1, and of the possible third driving line D1.
  • the driving line U1 conveys, on the corresponding influence area, a pressure signal substantially corresponding to the pressure in the cylinder 20 (designated in what follows by p 20 - likewise, p 22 and p 24 will be used for the cylinders 22, 24); namely, it substantially conveys information regarding a delivery pressure of the cylinder 20 immediately downstream thereof and upstream of the corresponding delivery valve 26.
  • the driving line CV1 conveys on the corresponding influence area a pressure signal corresponding to the pressure inside the control volume CV, designated in what follows by p CV .
  • the driving line D1 conveys on the corresponding influence area a pressure signal corresponding to the pressure that is exerted on the delivery port 4, which in this case is substantially equal to the pressure within the common rail CR, designated in what follows by p CR .
  • the common rail CR is in fact hydraulically connected to the delivery port 4, which is in turn hydraulically connected to the delivery line 32 by means of the second manifold channel 38.
  • actuation force associated to the hydraulic driving line D1 can be the result, in some embodiments, of the geometry of the delivery valve that offers to the fluid within it an influence area by means of which it is possible to exert a force on the mobile element of the delivery valve itself.
  • the control volume CV is in this operating condition a stagnant environment, in so far as there is no passage of flow through the hydraulic control line 39 since the control valve 42 is in a position of complete closing.
  • the delivery valve 26 can be assimilated to a conventional non-return valve; i.e., the delivery valve 26 remains open until the pressure within the cylinder 20 (p 20 ) exceeds the pressure p CV (which is equal, in these conditions, to the pressure p CR ) by an amount sufficient to overcome the action of contrast of the elastic element S1, which can be expressed, as is known, by means of an equivalent pressure.
  • the difference between the pressure p 20 and the equivalent pressure associated to the elastic element S1 must be equal to or higher than the pressure p CR .
  • Opening of each delivery valve starts at the end of the compression phase performed by the corresponding piston, and terminates a few instants after the top dead centre TDC, at the end of the reflux phase.
  • the pressure p CR has undergone an increase such that it is very close to the threshold pressure p REF ( Figure 7 ).
  • the excess flowrate delivered by the pump 1 to the common rail CR is not consumed by the injectors connected thereto and results in an accumulation of fluid that raises the level of pressure within the common rail CR and, ultimately, on the delivery port 4.
  • the overstepping of the threshold pressure p REF occurs, with reference to Figures 4 to 8 and in particular to Figure 7 , at an angle of rotation CA IS,R .
  • the angle CA IS,R falls within the delivery phase of the piston P3.
  • the overstepping of the threshold pressure p REF within the common rail CR is detected, in this embodiment, by the electronic control unit 46 by pressure-sensor means of a known type operatively connected thereto and installed on the common rail CR (a schematic functional representation of the operative connection between said sensor means and the control unit 46 is represented by a dashed and dotted line joining the control unit 46 and the common rail CR and designated by the reference PRS).
  • the control unit 46 hence controls an actuation of the solenoid 44 that causes the opening of the control valve 42.
  • a flow passage is set up in the control line 39 from the delivery port 4 to the control volume CV through the choke 40 and from the control volume CV to the manifold channel 6 through the return line 43.
  • the flow passage through the choke 40 causes a descent of the value of the pressure p CV certainly below the value of the pressure p CR since on account of the flow passage through the choke 40 a pressure drop is induced into the fluid, which upstream of the choke has precisely the pressure p CR .
  • the presence of the choke 40 enables said regulation to be obtained by draining flowrates that are very small as compared to the ones processed by the pump, to the advantage of the hydraulic efficiency of the pump itself.
  • the control assembly of the pump 1 controls the valve 42 so as to prevent the pressure p CV in the control volume CV from exceeding the pressure p REF .
  • the control valve 42 is arranged, once the threshold pressure p REF in a user connected to the delivery port 4 of the pump 1 (in this case, the common rail CR) is exceeded, for regulating the pressure in the control volume CV, limiting it to a value at the most equal to p REF .
  • any known means designed to regulate the pressure in the control volume CV, preventing the rising thereof beyond a threshold value (p REF , in the case in subject) can be used for implementing the regulation mechanism described herein.
  • the delivery valve 30 is always subject to the action of the hydraulic driving lines U3, D3 (if present) and CV3, but now the pressure signal conveyed onto the valve 30 by the driving line CV3 is lower than the one conveyed by the driving lines U3 (and D3, if present), which are always equal to the pressure p CR .
  • the conditions for equilibrium of the delivery valve 3 hence change and are such that it remains open even when the pressure p 24 drops below the pressure in the delivery environment (p CR ). In other words, the delivery valve 30 is kept in the open position also during at least part of the descent phase of the piston P3.
  • This causes a reflux of fluid from the delivery port 4 to the cylinder 24, causing, in the last analysis, a reduction of the pressure p CR within the common rail CR on account of the reduction of the accumulation of fluid.
  • the delivery valve 30 closes, and in the corresponding cylinder 24 the phase of expansion of the fluid contained therein starts, followed by the intake phase.
  • control assembly of the pump 1 is substantially arranged for keeping the delivery valve 30 (and, with the due timing, the delivery valves 26, 28) in the open position also following upon the delivery phase, i.e., during at least part of the descent phase of the piston P3, by regulation of the pressure p CV (associated to the driving lines CV1, CV2, CV3), in particular by limitation of the pressure p CV to the value of the threshold pressure p REF if said threshold pressure p REF is exceeded in a user (in this case, the common rail CR) hydraulically connected to the delivery port 4.
  • the pressure p CV associated to the driving lines CV1, CV2, CV3
  • the regulation system proposed herein is such that in conditions of full-flowrate operation each delivery valve remains open for a little less than half of the working cycle, basically corresponding to the delivery phase (the reflux phase is substantially negligible).
  • the instant of closing is decidedly delayed, and this results in an additional angular range of opening, where there is witnessed an increase in the reflux of flowrate through the delivery valve 30 (points of the curve with negative ordinates), which indicates the occurrence of a considerable reflux of fuel back into the cylinder 24.
  • the fluid returns to the pump the excess work of compression performed in the preceding delivery phase, thus guaranteeing a good level of energy efficiency of the entire system.
  • the regulation of the flowrate sent by the pump 1 is obtained by reflux of fluid (in particular fuel) to the delivery of each piston.
  • the pump 1 according to the present invention hence presents a series of considerable advantages over pumps of a known type.
  • the pump 1 enables the elimination of the need for expensive regulations by lamination at the delivery or for dangerous regulations by lamination at the intake, which are the source of problems connected to cavitation in the fluid induced thereby.
  • control assembly of the pump 1 is easy to manage and moreover enables regulation of the threshold pressure within the common rail CR in a simple way by acting on the calibration/threshold of opening of the control valve 42.
  • the flowrate consumed by the control system is moreover very small and substantially negligible as compared to the one typically processed by the pump 1, which minimizes the impact of the operation of the control system on the operation of the pump 1 itself.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Reciprocating Pumps (AREA)

Claims (9)

  1. Hydraulische Pumpe (HP; 1), insbesondere Kraftstoffpumpe, umfassend:
    eine Einlassöffnung (IP; 2),
    eine Abgabeöffnung (DP; 4), die zur hydraulischen Verbindung mit einem Anwender (U; CR) angeordnet ist,
    wenigstens einen Zylinder (CY; 20, 22, 24), in dessen Innerem ein entsprechender Kolben (P; P1, P2, P3) beweglich ist, wobei der Kolben während des Betriebes der Pumpe (HP, 1) eine Pendelbewegung zwischen einem oberen Totpunkt (TDC) und
    einem unteren Totpunkt (BDC) aufweist,
    ein Abgabeventil (DV; 26, 28, 30) für jeden Zylinder (CY; 20, 22, 24), das mit diesem verbunden und zwischen einer geschlossenen Position und einer offenen Position beweglich ist, wobei in der offenen Position das Abgabeventil (DV; 26, 28, 30) dafür angeordnet ist, einen Fluss von Fluid zwischen dem Zylinder (CY; 20, 22, 24) und der Abgabeöffnung (DP; 4) zu ermöglichen, und wobei in der geschlossenen Position das Abgabeventil (DV; 26, 28, 30) dafür angeordnet ist, einen Fluss von Fluid zwischen dem Zylinder (CY; 20, 22, 24) und der Abgabeöffnung (DP; 4) zu sperren, wobei während des Betriebes der Pumpe (HP, 1) das Abgabeventil während eines Teiles der Bewegung des Kolbens von dem unteren Totpunkt (BDC) zu dem oberen Totpunkt (TDC) in der offenen Position ist und nach dem oberen Totpunkt (TDC) der Pendelbewegung des Kolbens (P; P1, P2, P3) schließt, wobei die Pumpe (HP, 1) dadurch gekennzeichnet ist, dass sie eine Regulieranordnung (R; 39, 40, 42, 43, 44, 46) umfasst, die, wenn ein Schwellendruck (pREF) in einem hydraulisch mit der Abgabeöffnung (DP; 4) verbundenen Anwender (U; CR) überschritten wird, dafür angeordnet ist, das Abgabeventil (DV, 26, 28, 30) wenigstens während eines Teiles der Bewegung des Kolbens von dem oberen Totpunkt (TDC) zu dem unteren Totpunkt (BDC) in der offenen Position zu halten, wodurch das Schließen des Abgabeventils (DV, 26, 28, 30) verzögert und ein Rückfluss von Fluid von der Abgabeöffnung (4, DP) zu dem Zylinder (20, 22, 24) ermöglicht wird.
  2. Hydraulische Pumpe (1) nach Anspruch 1, dadurch gekennzeichnet, dass das Abgabeventil (26, 28, 30) mittels hydraulischer Antriebsleitungen (U1, U2, U3; D1, D2, D3; CV1, CV2, CV3) gesteuert wird.
  3. Hydraulische Pumpe (1) nach Anspruch 2, dadurch gekennzeichnet, dass die Regulieranordnung (R; 39, 40, 42, 43, 44, 46) umfasst:
    ein Steuervolumen (CV) in Fluidverbindung mit der Abgabeöffnung (4) mittels einer hydraulischen Steuerleitung (39), an die eine Drossel (40) gesetzt ist; und
    ein Steuerventil (42), das zum Regulieren eines Druckes (pCV) in dem Steuervolumen (CV) angeordnet ist und dafür betätigt werden kann, eine Fluidkommunikation zwischen dem Steuervolumen (CV) und der Einlassöffnung (2) zu ermöglichen,
    wobei die Drossel (40) hydraulisch stromaufwärts von dem Steuervolumen (CV) gesetzt ist.
  4. Hydraulische Pumpe (1) nach Anspruch 3, dadurch gekennzeichnet, dass die hydraulischen Antriebsleitungen umfassen:
    eine erste hydraulische Antriebsleitung (U1, U2, U3), die an das Abgabeventil (26, 28, 30) ein Drucksignal liefert, das im Wesentlichen einem Druck (p20, p22, p24) in dem wenigstens einen Zylinder (20, 22, 24) entspricht,
    eine zweite hydraulische Antriebsleitung (CV1, CV2, CV3), die an das Abgabeventil (26, 28, 30) ein Drucksignal liefert, das im Wesentlichen einem Druck (pCV) im Inneren des Steuervolumens (CV) entspricht.
  5. Hydraulische Pumpe (1) nach Anspruch 4, dadurch gekennzeichnet, dass das Steuerventil (42) dafür angeordnet ist, den Druck (pCV) in dem Steuervolumen (CV) bei Überschreiten des Schwellendruckes (pREF) in einem hydraulisch mit der Abgabeöffnung (DP; 4) verbundenen Anwender (U; CR) im Wesentlichen auf den Wert des Schwellendrucks (pREF) zu begrenzen.
  6. Hydraulische Pumpe (1) nach einem der Ansprüche 2 bis 5, dadurch gekennzeichnet, dass das Abgabeventil (26, 28, 30) eine dritte hydraulische Antriebsleitung (D1, D2, D3) umfasst, die an das Abgabeventil (26, 28, 30) ein Drucksignal liefert, das im Wesentlichen einem Druck (pCR) an der Abgabeöffnung (4) entspricht, wobei die dritte hydraulische Antriebsleitung (D1, D2, D3) dafür angeordnet ist, das Abgabeventil (26, 28, 30) in die offene Position zu bringen.
  7. Hydraulische Pumpe (1) nach Anspruch 6, dadurch gekennzeichnet, dass die zweite hydraulische Antriebsleitung (CV1, CV2, CV3) an einer Wirkfläche gleich der Summe von jeweiligen Wirkflächen wirkt, an denen die ersten (U1, U2, U3) und dritten (D1, D2, D3) hydraulischen Antriebsleitungen wirken.
  8. Hydraulische Pumpe (1) nach Anspruch 3, dadurch gekennzeichnet, dass das Steuerventil (42) mittels einer elektronischen Steuereinheit (46) gesteuert wird, die dafür angeordnet ist, mit Sensormitteln zum Erfassen des Druckes in einem mit der Abgabeöffnung (4) verbundenen Anwender (U; CR) zusammenzuwirken.
  9. Hydraulische Pumpe (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sie einen ersten Kolben (P1), einen zweiten Kolben (P2) und einen dritten Kolben (P3) umfasst, die funktionell bezugsrichtig einem ersten Abgabeventil (26), einem zweiten Abgabeventil (28) und einem dritten Abgabeventil (30) zugeordnet sind, wobei die ersten, zweiten und dritten Kolben (P1, P2, P3) mittels einer Pendelbewegung durch einen Eingabeschaft bzw. eine Eingabewelle (IS) der hydraulischen Pumpe (1) angetrieben werden.
EP20110157051 2011-03-04 2011-03-04 Hydraulikpumpe, insbesondere eine Kraftstoffpumpe Active EP2495431B1 (de)

Priority Applications (5)

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DK11157051T DK2495431T3 (da) 2011-03-04 2011-03-04 Hydraulisk pumpe, i særdeleshed en brændstofpumpe
EP20110157051 EP2495431B1 (de) 2011-03-04 2011-03-04 Hydraulikpumpe, insbesondere eine Kraftstoffpumpe
JP2012035345A JP5866225B2 (ja) 2011-03-04 2012-02-21 油圧ポンプ、特に燃料ポンプ
KR1020120021829A KR101540502B1 (ko) 2011-03-04 2012-03-02 수압식 펌프, 특히 연료 펌프
CN201210052526.5A CN102654091B (zh) 2011-03-04 2012-03-02 特别是燃料泵的液压泵

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20110157051 EP2495431B1 (de) 2011-03-04 2011-03-04 Hydraulikpumpe, insbesondere eine Kraftstoffpumpe

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EP2495431B1 true EP2495431B1 (de) 2014-01-15

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PT2902628T (pt) * 2012-09-25 2018-06-06 Sun Wei Bomba hidráulica alternativa de baixa velocidade para carga pesada com área de atuação variável

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JPS55160187A (en) * 1979-05-31 1980-12-12 Toyoda Autom Loom Works Ltd Compressor
DE3023731A1 (de) * 1980-06-25 1982-01-14 Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh, 7990 Friedrichshafen Einspritzpumpe
DE3417210A1 (de) * 1984-05-10 1985-11-14 Robert Bosch Gmbh, 7000 Stuttgart Druckventil
JPS6155382A (ja) * 1984-08-27 1986-03-19 Mitsui Eng & Shipbuild Co Ltd 往復動型圧縮装置及びその圧縮方法
EP0752061B1 (de) * 1994-03-23 1999-01-27 Siemens Aktiengesellschaft Anordnung zur einspritzung von kraftstoff in die zylinder einer brennkraftmaschine
JPH10318060A (ja) * 1997-05-22 1998-12-02 Toyota Motor Corp 蓄圧式燃料噴射装置
JP2000240528A (ja) * 1999-02-18 2000-09-05 Toyota Motor Corp 内燃機関の燃料噴射制御装置
GB0221165D0 (en) * 2002-09-12 2002-10-23 Artemis Intelligent Power Ltd Fluid-working machine and operating method
EP1411238B1 (de) * 2002-10-15 2006-01-11 Robert Bosch Gmbh Druckbegrenzungsventil für ein Kraftstoffeinspritzsystem
DE10327411B4 (de) * 2002-10-15 2015-12-17 Robert Bosch Gmbh Druckbegrenzungsventil sowie Kraftstoffsystem mit einem solchen Druckbegrenzungsventil
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JP4861958B2 (ja) * 2007-10-31 2012-01-25 日立オートモティブシステムズ株式会社 高圧燃料ポンプ

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JP2012184761A (ja) 2012-09-27
CN102654091B (zh) 2016-07-06
KR20120100804A (ko) 2012-09-12
DK2495431T3 (da) 2014-02-03
KR101540502B1 (ko) 2015-07-29
CN102654091A (zh) 2012-09-05
EP2495431A1 (de) 2012-09-05
JP5866225B2 (ja) 2016-02-17

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