EP3207254B1 - Steuerungssystem und verfahren zur steuerung einer positiven verdrängerpumpe - Google Patents

Steuerungssystem und verfahren zur steuerung einer positiven verdrängerpumpe Download PDF

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Publication number
EP3207254B1
EP3207254B1 EP15775819.4A EP15775819A EP3207254B1 EP 3207254 B1 EP3207254 B1 EP 3207254B1 EP 15775819 A EP15775819 A EP 15775819A EP 3207254 B1 EP3207254 B1 EP 3207254B1
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EP
European Patent Office
Prior art keywords
fluid
configuration
thrust chamber
pump
control means
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EP15775819.4A
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English (en)
French (fr)
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EP3207254A1 (de
Inventor
Leonardo Cadeddu
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VHIT SpA
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VHIT SpA
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member

Definitions

  • the object of the present invention is a control system and method for controlling a variable volume positive displacement rotary pump.
  • variable displacement pumps for circulation of the lubrication oil in an internal combustion engine and any possible auxiliaries.
  • Variable displacement makes it possible to regulate the flow rate of the lubrication oil, optimizing it based on the operating mode of the engine.
  • the flow rate should be such as to ensure adequate lubrication at low speeds, but this would determine an excessive flow rate at higher speeds (therefore requiring greater consumption by the engine to ensure circulation of the lubricant and imposing higher pressures and thus greater stress on the circuit).
  • variable displacement pump for circulation of lubrication oil
  • two chambers are shown that move a stator, inside of which a vane rotor rotates.
  • the movement of the stator determines a variation in the output of the pump.
  • Access to at least one of the two thrust chambers is regulated by a valve controlled by an electronic control unit.
  • the two thrust chambers act jointly to counter the force exerted by a spring.
  • the spring exerts a force that pushes the stator to a position of maximum displacement.
  • variable displacement pump A further example of a variable displacement pump is disclosed in document US 2014/0219847 A1 .
  • variable displacement pump when utilized on mid-range/high-powered engines for heavy vehicles there is a problem consisting of a marked delay in the increase in flow rate/pressure of the oil needed for quickly activating the actuator of the engine brake and for protecting the internal members of the engine from stress.
  • the technical task underlying the present invention is to offer a control system and method for controlling a pump that make it possible to overcome the drawbacks described hereinabove.
  • an aim of the present invention is to offer a control system and method for controlling a pump that make better lubrication of a load possible, regardless of the operating conditions.
  • control system for controlling a positive displacement pump is indicated by the reference number 1.
  • This system comprises the positive displacement pump 2, which is of the variable volume rotary type.
  • variable displacement makes it possible to optimize operation under different operating conditions.
  • the pump 2 comprises a stator 20 that is movable so as to determine a variation in the volume of the pump 2.
  • the stator 20 is conveniently hollow and a rotor 200, typically a vane rotor, is present inside the stator. Relative movement of the stator 20 with respect to the axis of rotation of the rotor 200 allows for variation in the volume of the pump 2.Movement of the stator 20 can be of various types, for example it could be a tilting, rotational, or translational type of movement.
  • the movement of the stator 20 is of the rotational type where a first, a second and a third arc are indicated by reference numbers 203, 204, 205, with a common centre, on which the stator 20 rotates.
  • the pump 2 further comprises a first thrust chamber 214 for thrusting the stator 20.
  • This first thrust chamber 21 is designed to be filled with a fluid processed by the pump. In this manner, it is possible to bring about movement of the stator 20 and a variation in the volume of the pump 2.
  • the fluid processed by the pump 2 is a liquid, typically oil. Therefore, this fluid is not compressible.
  • the first chamber 21 is defined by the fluid dynamic seal realized with the contribution of the third arc 205, the first arc 203 and the gasket 201.
  • the system 1 comprises a supply line 3 for supplying the fluid processed by the pump 2 to a load.
  • the load is generally indicated by the reference letter "C", for example the lubrication system of an endothermic engine.
  • the supply line 3 extends downstream of a delivery side of the pump 2; it preferably starts precisely from the delivery side of the pump 2.
  • the system 1 conveniently comprises an element 4 that defines a localized pressure drop.
  • This element 4 is located along the supply line 3. It is located before the load.
  • the element 4 that defines a localized pressure drop advantageously consists in a filter 40 for the fluid in transit in said supply line 3.
  • the filter 40 determines a pressure drop that can amount to as much as 2-3 bars, based on temperature, flow rate and blockage.
  • the filter 40 lies along the supply line 3.
  • the element 4 could also consist in a component of another type that determines an abrupt localized type of pressure loss.
  • the system 1 also comprises control means 5 for controlling the flow of the fluid supplying said first chamber 21.
  • control means 5 is able to assume at least a first and a second configuration.
  • the system 1 further comprises a first branch 31, which, in the first configuration of the control means 5, allows for collecting the fluid (pressure) to be directed into the first thrust chamber 21, from said supply line 3 downstream of said element 4 (see Figure 1 ).
  • the system 1 further comprises a second branch 32, which, in the second configuration of the control means 5, allows for collecting the fluid (pressure) to be directed into the first thrust chamber 21, from said supply line 3 upstream of said element 4 (see Figure 2 ).
  • a second branch 32 which, in the second configuration of the control means 5, allows for collecting the fluid (pressure) to be directed into the first thrust chamber 21, from said supply line 3 upstream of said element 4 (see Figure 2 ).
  • the contour of the stator 20 is illustrated in the schematic view of Figure 1 and the rotor 200 is visible only in Figure 2 .
  • the second configuration enables a more demanding functioning of the load (for example this can involve operating conditions in which the engine brake is activated or mid-range/high-powered engines are operating on heavy vehicles).
  • the second branch 32 is conveniently connected to a maximum pressure safety valve 511. In the case of excess pressure, this valve 511 enables the fluid to be discharged into a collection system (which is, in turn, operatively connected to the suction of the pump 2).
  • control means 5 conveniently enables passage of the fluid from said first branch 31 towards the first thrust chamber 21, blocking passage of the fluid from said second branch 32 towards the first thrust chamber 21.
  • the movement of the fluid in the first configuration of the control means is illustrated in Figure 1 .
  • control means 5 In the second configuration ( Figure 2 ), the control means 5 enables passage of the fluid from said second branch 32 towards the first thrust chamber 21, blocking passage of the fluid from said first branch 31 towards the first thrust chamber 21.
  • the movement of the fluid in the second configuration of the control means is illustrated in Figure 2 .
  • the control means 5 for controlling the flow of the fluid comprises a three-way valve 50 that alternatively has the first or second branch 31, 32 as inlets.
  • This three-way valve 50 is typically responsible for the occurrence of the first or second configuration of the control means 5.
  • the system 1 conveniently comprises an electronic control unit 6 for commanding the flow control means 5, said electronic control unit 6 determining the switching between the first and the second configuration.
  • the control means 5 for controlling the flow comprises a modulating valve 51 for modulating the entrance of fluid into the first thrust chamber 21.
  • the valve 51 could consist of a spool valve.
  • the outlet of said three-way valve 50 supplies the inlet of the spool valve.
  • the modulating valve 51 (the spool valve) comprises piston that moves in a compartment. In a first position of the piston, the modulating valve 51 enables the first chamber 21 to be filled. In a second position of the piston, the regulating valve enables the first chamber 21 to be emptied. Conveniently, in the second position of the piston, the fluid present in the first chamber 21 is re-directed towards the suction of the pump 2.
  • the modulating valve 51 is controlled by the electronic control unit 6.
  • the system 1 conveniently comprises a second thrust chamber 22.
  • the second chamber 22 is found (is supplied) downstream of said element 4, with respect to the direction of travel of the fluid in the supply line 3.
  • the second thrust chamber 22 is supplied by a third branch 33 located downstream of said element 4.
  • the third branch 33 conveniently extends from the supply line 3.
  • the third branch 33 extends upstream of the load C that is supplied by the line 3.
  • the fluid present in the second thrust chamber 22 exerts an opposite thrust on the stator 20 with respect to the fluid present in the first thrust chamber 21.
  • the pump 2 comprises elastic means 23 that exerts an action jointly with the fluid present in the first thrust chamber 21 so as to position the stator 20 in the maximum volume configuration.
  • the elastic means 23 comprises for example a compression spring. Leaving the condition of maximum volume, the spring is compressed. In this manner, even in the case where there is a breakdown in the electronics management of the control system of the pump 2, the latter progresses towards a situation of maximum volume, minimizing the risk of "seizing".
  • the third branch 33 conveniently keeps the second chamber 22 pressurized.
  • the second chamber 22 is defined by the fluid dynamic sealing realized with the contribution of the third arc 205, the second arc 204 and the gasket 202.
  • the object of the present invention is also a method for controlling the operation of a variable volume positive displacement rotary pump.
  • the control method is conveniently implemented by a control system 1 that has one or more of the characteristics described hereinabove.
  • the method of operation of the system 1 shall thus be illustrated by way of example below.
  • the method comprises the stage of conveying a fluid exiting from the delivery side 24 of the pump 2 along a supply line 3 for supplying a load C, having it pass through at least one filter 40.
  • the load C typically comprises a lubrication system for an internal combustion engine.
  • This filter 40 determines a drop in pressure that can amount to as much as 2-3 bars.
  • the method further comprises the stage of positioning the control means 5 for controlling the flow of fluid in a first configuration in such a manner as to collect part of the fluid in transit along said supply line 3, downstream of the filter 40, and convey it into a first thrust chamber 21 for thrusting a stator 20 (see Figure 1 ).
  • the stage of positioning the control means 5 for controlling the flow of fluid in a first configuration comprises positioning a three-way valve 50 so that part of the fluid in transit along said supply line 3 is collected downstream of the filter 40 ( Figure 1 ).
  • the stage of positioning the control means 5 in the first configuration further comprises having the fluid exiting the three-way valve 50 pass through a spool valve 51 that regulates/modulates access of the fluid into the first chamber 21.
  • the method conveniently comprises the stage of conveying part of the fluid that has passed from the delivery side of the pump 2 into a second chamber 22.
  • the pressure exerted on the stator 20 by the fluid in the first chamber 21 is opposite the pressure exerted on the stator 20 by the fluid present in the second chamber 22.
  • the method comprises exerting, by means of the elastic means 23, a force on the stator 20 that opposes the distancing of the stator 20 from a position associated with the maximum volume of the pump 2.
  • the position of the stator 20 is conveniently defined by the equilibrium at least of the following stresses:
  • the pressure exerted on the stator 20 by the fluid present in the first chamber 21 is opposite the force exerted on the stator 20 by the elastic means 23.
  • the method further comprises the stage of changing the configuration of the flow control means 5 so as to pass from the first configuration to a second configuration. Passage from the first to the second configuration is associated with a configuration for more demanding functioning (for example, but not necessarily, frequent recourse to the engine brake). Conveniently, passage from the first to the second configuration is determined by a command coming from an electronic control unit based on the detection of certain input signals (for example through sensors or an explicit user command).
  • the method comprises the stage of collecting a working fluid between the delivery side 24 of the pump 2 and the filter 40 and directing it to the first thrust chamber 21 (see Figure 2 ).
  • the passage from the first to the second configuration determines a movement of the stator 20 accompanied by a rapid increase in the volume of the pump 2.
  • the pressure that is available and that can be modulated for said first chamber 21 is higher than in the first configuration.
  • the stage of changing the configuration of the control means 5 so as to pass from the first to the second configuration advantageously comprises changing the configuration of the three-way valve 50 so that a fluid passes through it, the fluid being the fluid that is collected from the supply line 3 supplying the load downstream of the delivery side of the pump 2, but before the filter 40.
  • stator 20 can progress towards a position with which the maximum volume of the pump 2 is associated, thus ensuring a greater fluid flow rate so as to meet more demanding functioning needs.
  • the latter can exert greater pressure with respect to the second thrust chamber (and this makes the passage of the stator into the maximum volume configuration faster, preventing, among other things, vibrations or undesired reactions).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (10)

  1. Steuersystem, umfassend:
    - eine Verdrängerkreiselpumpe (2) mit variablem Volumen, die wiederum umfasst:
    I) einen Stator (20), der derart beweglich ist, dass eine Schwankung des Volumens der Pumpe (2) bestimmt wird,
    II) eine erste Schubkammer (21), um den Stator (20) vorzudrücken und dafür gestaltet, mit einem Fluid gefüllt zu werden, das von der Pumpe verarbeitet wird, so dass eine Bewegung des Stators (20) und eine Schwankung des Volumens der Pumpe (2) bestimmt wird,
    - eine Speiseleitung (3) zum Speisen des Fluids, das von der Pumpe (2) verarbeitet wird, zu einer Last,
    - ein Element (4), das einen lokalisierten Druckabfall definiert, wobei sich das Element (4) entlang der Zufuhrleitung (3) befindet,
    - ein Steuermittel (5) zum Steuern des Strömens des Fluids, das die erste Kammer (21) speist, wobei das Steuermittel (5) in der Lage ist, mindestens eine erste und eine zweite Gestaltung einzunehmen,
    eine erste Abzweigung (31), die in der ersten Gestaltung des Steuermittels (5) ermöglicht, das Fluid, das aus der Speiseleitung (3) stromabwärts des Elements (4) gesammelt wird, in die erste Schubkammer (21) zu lenken,
    eine zweite Abzweigung (32), die in der zweiten Gestaltung des Steuermittels (5) ermöglicht, das Fluid, das aus der Speiseleitung (3) stromaufwärts des Elements (4) gesammelt wird, in die erste Schubkammer (21) zu lenken, wobei die zweite Gestaltung im Verhältnis zur ersten Gestaltung das Funktionieren der Last unter anspruchsvolleren Bedingungen ermöglicht.
  2. System nach Anspruch 1, dadurch gekennzeichnet, dass das Element (4), das einen lokalisierten Druckabfall definiert, aus einem Filter (40) für das Fluid beim Durchqueren der Speiseleitung (3) besteht.
  3. System nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass das Steuermittel (5):
    - in der ersten Gestaltung das Hindurchtreten des Fluids von der ersten Abzweigung (31) zur ersten Schubkammer (21) ermöglicht und dabei das Hindurchtreten des Fluids von der zweiten Abzweigung (32) zur ersten Schubkammer (21) blockiert,
    - in der zweiten Gestaltung das Hindurchtreten des Fluids von der zweiten Abzweigung (32) zur ersten Schubkammer (21) ermöglicht und dabei das Hindurchtreten des Fluids von der ersten Abzweigung (31) zur ersten Schubkammer (21) blockiert.
  4. System nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Steuermittel (5) zum Steuern des Strömens des Fluids ein Dreiwegeventil (50) umfasst, das alternativ die erste oder die zweite Abzweigung (31, 32) als Einlass aufweist.
  5. System nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass es eine elektronische Steuereinheit (6) zum Beherrschen des Strömungssteuermittels (5) umfasst, wobei die elektronische Steuereinheit (6) das Umschalten zwischen der ersten und der zweiten Gestaltung bestimmt.
  6. System nach Anspruch 5, dadurch gekennzeichnet, dass das Steuermittel (5) zum Steuern der Strömung ein modulierendes Ventil (51) zum Modulieren des Einführens von Fluid in die erste Schubkammer (21) umfasst und das durch die elektronische Steuereinheit (6) gesteuert wird.
  7. System nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass es eine zweite Schubkammer (22) umfasst, wobei die zweite Schubkammer (22) sowohl in der ersten als auch der zweiten Gestaltung des Steuermittels (5) im Verhältnis zur Bewegungsrichtung des Fluids in der Speiseleitung (3) stromabwärts des Elements (4) liegt.
  8. System nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Fluid, das in der zweiten Schubkammer (22) vorhanden ist, einen im Verhältnis zu dem Fluid, das in der ersten Schubkammer (21) vorhanden ist, entgegengesetzten Schub ausübt, wobei die Pumpe (2) ein elastisches Mittel (23) umfasst, das gemeinsam mit dem Fluid, das in der ersten Schubkammer (21) vorhanden ist, eine Wirkung ausübt, so dass der Stator (20) in der Maximalvolumengestaltung positioniert wird.
  9. Verfahren zum Steuern des Betriebes einer Verdrängerkreiselpumpe mit variablem Volumen, die folgenden Schritte umfassend:
    - Befördern eines Fluids, das aus der Zufuhrseite (24) der Pumpe (2) austritt, entlang einer Speiseleitung (3) zum Speisen einer Last, wobei man das Fluid durch mindestens einen Filter (40) hindurchtreten lässt,
    - Positionieren des Steuermittels (5) zum Steuern der Strömung von Fluid in einer ersten Gestaltung derart, dass stromabwärts des Filters (40) ein Teil des Fluids beim Durchqueren entlang der Speiseleitung (3) gesammelt und in eine erste Schubkammer (21) befördert wird, um einen Stator (20) vorzudrücken,
    - Wechseln der Gestaltung des Steuermittels (5) zum Steuern der Strömung des Fluids derart, dass es von der ersten Gestaltung in eine zweite Gestaltung übergeht, so dass ein Sammeln eines Arbeitsfluids zwischen der Zufuhrseite (24) der Pumpe (2) und dem Filter (40) und das Lenken desselben in die erste Schubkammer (21) ermöglicht wird, wobei dies eine Bewegung des Stators (20) bestimmt, die von einer Zunahme des Volumens der Pumpe (2) begleitet wird, und im Verhältnis zu ersten Gestaltung die zweite Gestaltung das Funktionieren der Last unter anspruchsvolleren Bedingungen ermöglicht.
  10. Verfahren nach Anspruch 9, dadurch gekennzeichnet, dass mindestens in der ersten Gestaltung des Steuermittels (5) eine zweite Schubkammer (22), die einen Druck auf den Stator (20) ausübt, der dem Druck der ersten Schubkammer (21) entgegengesetzt ist, stromabwärts des Filters (40) gespeist wird.
EP15775819.4A 2014-10-15 2015-09-17 Steuerungssystem und verfahren zur steuerung einer positiven verdrängerpumpe Active EP3207254B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITPR20140069 2014-10-15
PCT/IB2015/057147 WO2016059490A1 (en) 2014-10-15 2015-09-17 Control system and method for controlling a positive displacement pump

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Publication Number Publication Date
EP3207254A1 EP3207254A1 (de) 2017-08-23
EP3207254B1 true EP3207254B1 (de) 2021-04-21

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WO (1) WO2016059490A1 (de)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10138187B4 (de) * 2001-07-27 2013-03-14 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Mengenregelbare Flügelzellenpumpe
ITBO20030528A1 (it) * 2003-09-12 2005-03-13 Pierburg Spa Impianto di pompaggio utilizzante una pompa a palette
WO2007087704A1 (en) 2006-01-31 2007-08-09 Magna Powertrain Inc. Variable displacement variable pressure vane pump system
CN103228917B (zh) * 2010-11-24 2016-01-13 皮尔伯格泵技术有限责任公司 可变排量的润滑剂泵
JP6004919B2 (ja) * 2012-11-27 2016-10-12 日立オートモティブシステムズ株式会社 可変容量形オイルポンプ

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WO2016059490A1 (en) 2016-04-21

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