EP2014919B1 - Soupape de réglage pour le réglage du volume d'alimentation d'une pompe volumétrique - Google Patents

Soupape de réglage pour le réglage du volume d'alimentation d'une pompe volumétrique Download PDF

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Publication number
EP2014919B1
EP2014919B1 EP08159994.6A EP08159994A EP2014919B1 EP 2014919 B1 EP2014919 B1 EP 2014919B1 EP 08159994 A EP08159994 A EP 08159994A EP 2014919 B1 EP2014919 B1 EP 2014919B1
Authority
EP
European Patent Office
Prior art keywords
valve
pump
fluid
adjusting
pressure
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.)
Not-in-force
Application number
EP08159994.6A
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German (de)
English (en)
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EP2014919B2 (fr
EP2014919A3 (fr
EP2014919A2 (fr
Inventor
Christof Dr. Lamparski
Jürgen Bohner
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Schwaebische Huettenwerke Automotive GmbH
Original Assignee
Schwaebische Huettenwerke Automotive GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by Schwaebische Huettenwerke Automotive GmbH filed Critical Schwaebische Huettenwerke Automotive GmbH
Priority to EP16206318.4A priority Critical patent/EP3173624B1/fr
Publication of EP2014919A2 publication Critical patent/EP2014919A2/fr
Publication of EP2014919A3 publication Critical patent/EP2014919A3/fr
Application granted granted Critical
Publication of EP2014919B1 publication Critical patent/EP2014919B1/fr
Publication of EP2014919B2 publication Critical patent/EP2014919B2/fr
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Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F04C14/185—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by varying the useful pumping length of the cooperating members in the axial direction
    • 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
    • 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
    • F04C2210/00—Fluid
    • F04C2210/14—Lubricant
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/18—Pressure
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/20—Flow
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86622—Motor-operated
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86694—Piston valve
    • Y10T137/86702—With internal flow passage

Definitions

  • the invention relates to an adjustment valve for the adjustment of the delivery volume of a positive displacement pump and a positive displacement pump with the adjustment valve, which is arranged for the adjustment of the delivery volume of a fluid to be delivered by the pump in a fluid circuit of the pump.
  • the invention accordingly also relates to the adjustment valve as such, as far as it is provided for the adjustment of the delivery volume of a positive displacement pump.
  • Positive displacement pumps deliver fluids at a volume flow proportional to the pump speed.
  • the delivery volume per revolution or reciprocating stroke, the so-called specific volume flow is constant or, in practice, can be regarded as constant, at least to a good approximation.
  • the constancy per revolution or stroke and, accordingly, the proportionality to the pump speed is troublesome, for example, in applications in which the unit to be supplied by the respective pump has a fluid requirement which is lower in one or more speed range (s) of the pump than that from the Proportionality resulting volumetric flow. Accordingly, in the respective speed range, the pump delivers a volume flow above the demand, which is dissipated with loss.
  • the problem is in the US 6 126 420 B already disclosed an internal gear pump with adjustable delivery volume to solve the problem.
  • the US Pat. No. 6,244,839 B1 also discloses an internal gear pump with adjustable delivery volume.
  • the inner gear is axially displaceable relative to the outer gear.
  • the inner gear is part of an axially displaceable adjusting unit, which is formed as a double-acting piston.
  • the adjusting unit is acted upon by a 4/3-way adjusting valve with the pumped fluid from the pump.
  • the adjustment valve has a valve housing and a valve piston axially reciprocating valve piston which is acted upon at one axial end with the funded fluid and at the other axial end with a pressure of the fluid counteracting force of a valve spring.
  • the position of the valve piston adjusts according to the balance of the force of the valve spring and the force generated by the fluid pressure.
  • the Adjustment valve is designed so that the adjustment of the pump moves on reaching a predetermined by the valve spring fluid pressure from an axial position for maximum delivery volume towards an axial position for minimum delivery.
  • the preload force of the valve spring is adjusted at the adjustment
  • a positive displacement pump with an adjusting valve is known, the movable valve piston for adjusting the delivery volume of the pump in an axial direction with fluid of the high pressure side of the pump and the fluid counteracting acted upon by a spring force.
  • a control device is provided for the adjusting valve, which exerts an additional force on the valve piston.
  • control means an electric stepping motor for adjusting the biasing force of the valve spring and a magnetic coil for generating an additional magnetic force are called.
  • the switched by means of the adjustment fluid flow acts on a displacement unit of the pump only in the direction of maximum delivery volume, while in the opposite direction always the pressure of the high pressure side acts.
  • a controllable lubricating oil pump with a flow regulator comprises a valve with an axially movable control piston.
  • the control piston works against the force of a spring which is supported on the side facing away from the control piston on a device which allows to extend the travel of the control piston or to adjust the spring force of the spring.
  • the EP 1 555 436 A2 describes a gear pump with flow control with a valve whose passage opening can be changed by a control unit.
  • the valve is a pulse width modeled solenoid valve which is operatively connected to flow control via a pressure transducer connected to the first pressure chamber of the pump with a controller coupled thereto.
  • the valve is an electrically controllable valve and comprises a valve body axially movable in the valve body with sections of different diameters, during their displacement slot-shaped control openings of the valve are released or closed.
  • the DE 31 09 045 A1 describes a controllable hydraulic pump with a control valve.
  • the valve is a 3/2-way valve, the switching of which is effected by the action of fluid pressure on the end face of a valve spool movably mounted in the valve.
  • the JP 57 131890 A describes a controllable feed pump with an adjustable by pressurizing valve.
  • Other relevant pumps are also in the US 7 726948 B2 . US Pat. No. 6,244,839 B1 and FR 2 326 600 A known.
  • the invention is based on a positive displacement pump for the supply of an aggregate with fluid, which has a pump housing with a delivery chamber and a delivery member movable in the delivery member, which acts directly on the fluid to convey it through the delivery chamber.
  • the delivery member may, upon execution of a conveying movement, the fluid alone or in cooperation with one or possibly several further delivery member (s) of an inlet of the delivery chamber while increasing the pressure through an outlet of the delivery chamber.
  • the inlet becomes a low pressure side and the outlet is assigned to a high pressure side of the pump.
  • the pump is preferably arranged in a closed fluid circuit, but in principle can also serve to convey the fluid in an open fluid circuit.
  • the pump When integrated in a closed fluid circuit, it draws the fluid on the low-pressure side from a reservoir through the inlet into the delivery chamber and conveys it on the high pressure side to the or possibly several to be supplied with the fluid unit (s). Downstream of the unit (s), the fluid returns to the reservoir, closing the fluid circuit.
  • the pump can be used, for example, to supply a hydraulic press with pressurized fluid.
  • it is installed in a motor vehicle or provided for installation in order to supply a motor vehicle driving the engine with lubricating fluid or an automatic transmission with hydraulic fluid.
  • the internal combustion engine drives the pump.
  • the displacement pump further comprises an adjustment valve, adjusted by means of which the delivery volume of the pump adapted to the needs of at least one unit to be supplied and the energy required for driving the pump can be preferably reduced accordingly.
  • the adjustment valve comprises a valve housing, a valve piston movable in the valve body, a valve spring and an adjusting device.
  • the valve piston has an active surface for a fluidic valve set pressure.
  • the valve spring is arranged so that it counteracts the total on the valve body, acting valve actuating pressure on the valve piston.
  • the specific volume flow of the pump is understood as such in preferred embodiments, in the case of a rotary pump, the volume flow per revolution and in the case of a reciprocating pump, the flow rate per stroke.
  • the pump may also be a fixed displacement pump and the adjustment valve may be disposed on the high pressure side of the pump as a bypass valve to deliver excess fluid being conveyed bypassing the at least one unit into the reservoir.
  • Such a bypass conveyance does not reduce the power consumption of the pump, but still ensures demand-based delivery. It is not in such embodiments, the delivery volume at the outlet of the delivery chamber, but that to the at least one aggregate funded delivery volume needs controlled or regulated.
  • a pump adjustable in its delivery volume with such a bypass valve by adjusting the volume flow per revolution or stroke via an adjusting valve according to the invention or otherwise and downstream of the pump, but upstream of the unit to be supplied, part of the pump the pump funded flow is diverted and unused returned to a reservoir.
  • the delivery volume of the pump as such, as seen directly at the outlet of the delivery chamber, adjusted by means of the adjustment valve.
  • an actuator is arranged movably in the pump housing, which can be acted upon in the direction of its mobility with a dependent on the need of at least one unit actuating force.
  • the actuator may be arranged in particular to an end face of the conveyor member or the conveyor member surrounding.
  • the actuator and the delivery member are in first variants part of an in the pump housing as a whole back and forth movable adjustment, for example, a linearly movable or pivotable or otherwise movable transversely to a rotation axis of the preferably rotatable conveyor member adjustment.
  • adjusting units describe, for example, the US 6 28.3 735 B1 for outside-axle, the US 6 126 420 B and US Pat. No. 6,244, 8.39 B1 for internal-axis pumps
  • the actuator is adjustable relative to the conveyor member and the pump housing.
  • the actuator of the second variant may in particular be a collar surrounding the conveyor member as known from vane pumps including vane pumps, rotary vane pumps and internal tame gear pumps to adjust the eccentricity to the conveyor member, for example by a linear lifting or pivotal movement of the actuator.
  • the actuating force is preferably generated fluidically by the actuator forming an actuating piston, which is acted upon by a pressurized fluid.
  • This pressure fluid can be branched off, in particular, on the high-pressure side of the pump and can be returned to the actuator via the adjustment valve as a partial flow of the total volume flow delivered by the pump.
  • the pressurized fluid which is applied to the actuator, but in principle can also another fluid, such as a fluid provided from a pressure reservoir or from another pump.
  • a partial flow of the fluid is conducted via the adjustment valve into the delivery chamber back to the low-pressure side in order to increase the degree of filling of delivery cells there, as described, for example, in US Pat US Pat. No. 6,935,851 B2
  • the delivery volume is also adjusted at the same time, whereby this type of adjustment with one of the other types mentioned above can also be realized in combination.
  • the Verstelleinriclttullg is formed so that it can adjust the valve piston in the direction of the force exerted by the valve actuating pressure on the valve body or against the valve actuating pressure. It preferably acts electromagnetically.
  • the word “or” here as well as assault otherwise in the sense of the invention encompasses the meaning of "either ......... or” and also the meaning of "and”, as far as the respective context not necessarily surrounds a limited meaning.
  • the adjustment means may be constructed to counteract or preferably counteract the force of the valve set pressure only in the same direction and the valve spring, and alternatively may be constructed to bias the valve piston both in and against the force of the valve set pressure can adjust.
  • valve actuating pressure and a force exerted by the adjusting device on the valve piston act together against the force of the valve spring. If the valve actuating pressure increases, the valve piston can be adjusted by means of a correspondingly smaller force of the adjusting device against the force of the valve spring.
  • the adjusting device for adjusting the valve piston is set up both in the direction of the valve set pressure and against the valve set pressure. If the adjustment device is a magnetic adjustment device with only a single magnetic coil, the magnetic coil can be repolished in such embodiments.
  • the adjustment device is a magnetic adjustment device with only a single magnetic coil, the magnetic coil can be repolished in such embodiments.
  • the adjustment device is a magnetic adjustment device with only a single magnetic coil, the magnetic coil can be repolished in such embodiments.
  • the adjustment device is a magnetic adjustment device with only a single magnetic coil
  • the magnetic coil can be repolished in such embodiments.
  • the position of the valve piston can thus be adjusted relative to the valve housing, at least in the second embodiment, but preferably also in the first embodiment, independently of the force acting on the active surfaces Ventilstelltik, and the delivery volume of the pump can be adjusted accordingly.
  • the adjustment valve can thus adjust the delivery volume over a larger operating range of the unit to be supplied in a continuously or arbitrarily stepped manner and not only to a specific pressure at which the delivery volume is reduced.
  • a control or regulation device for the adjustment valve is set up so that by means of the adjustment valve the delivery volume can be adjusted adjusted over the entire operating range of the unit.
  • the invention combines an accurate and flexible Anpassbarlceit to the needs with a guaranteed even in case of failure of the adjustment supply security, it creates a so-called second-level control or regulation of the delivery volume.
  • the adjusting valve is preferably a proportional valve. It is preferably controlled electrically.
  • the adjusting device preferably acts magnetically. It may comprise a proportional solenoid which is voltage or current controlled or regulated, that is to say by a variation of the applied voltage or of the electric current oriented on the requirement of the at least one aggregate.
  • the adjustment valve is controlled or regulated by pulse modulation.
  • pulse modulation When using a pulse-modulated adjustment valve, the duration of the individual pulses or the time interval between two successive pulses of the manipulated variable can be varied, which also includes the case that both the pulse duration and the Time between each other following pulses is adjusted to the needs.
  • the period of the manipulated variable is preferably constant.
  • a pulse width modulated adjustment valve is used.
  • the period of the manipulated variable for the adjustment valve is significantly smaller than the time constant of the positive displacement pump which determines the adjustment of the delivery volume.
  • the pulse modulation uses the Tiefpass characters the pump. By varying the on-time of the pulse width modulation or the time interval in the case of a pulse frequency modulation adapted to the needs, the flow through the adjustment valve and consequently the displacement of the positive displacement pump can be quasi-continuously controlled or regulated according to the momentary demand of the unit.
  • the Veistellventil is preferably a multi-way valve with at least three ports, preferably with four ports. It is preferably switchable between at least two switch positions, preferably between three switch positions.
  • the adjustment valve is controlled or regulated in preferred embodiments in response to a desired value for the volume flow to be delivered by the positive displacement pump or a fluid supply pressure to be generated by the positive displacement pump.
  • a setpoint specification specifies the setpoint value of a control or regulation device provided for the adjustment valve. The set point is preferably varied depending on the demand of the unit. Preferably, a characteristic field is specified for the setpoints dependent on the operating state of the unit.
  • the at least one desired value or more preferably the plurality of desired values is or are predefined as a function of a physical variable characterizing the operating state, which is sensed during operation of the unit by means of a detection device.
  • the at least one physical variable may in particular be a temperature, a rotational speed or a load state of the aggregate.
  • the desired value or the desired values for the volume flow or the fluid supply pressure are predefined as a function of at least two variables characterizing the operating state of the unit. If the positive displacement pump is used as a lubricating oil pump for an internal combustion engine, the temperature of the lubricating oil or of the cooling fluid in the region of the internal combustion engine or the speed or for the load state can detect or determine the accelerator pedal position or throttle position, and from this using the characteristic field of the corresponding Determined setpoint and the control or regulating device for the adjustment valve can be specified.
  • the adjustment valve is only controlled as a function of the respective desired value.
  • the detection of an actual value representative of the requirement of the physical quantity forming the desired value, namely of the volume flow or of the fluid supply pressure, is dispensed with, as well as elaborate processing for a control based on a desired / actual comparison.
  • the adjustment valve is regulated as a function of a desired / actual comparison of the respective setpoint value and an actual value of the volume flow or the fluid supply pressure measured continuously or at sufficiently small time intervals.
  • a control is in such cases of Vorhausen, in which the volumetric flow demand of the unit changes due to wear over the life of the unit.
  • a control device which can switch from a controller according to the first embodiment to a control according to the second embodiment.
  • the adjustment valve is initially controlled on the basis of the predefined volumetric flow and, with increasing leakage losses as a result of wear of the unit, is later converted to pressure regulation.
  • a conductive control device is provided, which detects increasing wear based on a sensory detection of the volume flow or fluid supply pressure and the setpoint or the setpoint characteristic adjusted at least once or in several stages, possibly continuously shifts during the life of the unit.
  • the adjustment valve is firstly controlled and additionally energized by means of a nominal value or a nominal value map for the fluid supply pressure or the volume flow.
  • a particularly preferred embodiment is one based on one or more desired values or a setpoint characteristic map for the fluid supply pressure or the volume flow by means of Pulse width modulation controlled and additionally current controlled adjustment valve.
  • the control or regulating device may be integrated part of the adjustment valve or installed separately from it.
  • the setpoint specification can be embodied component of the control or regulation device or representational separately from the other parts of the control or regulating device.
  • the adjustment valve is preferably an integral part of the positive displacement pump, for example, mounted on the pump housing.
  • the adjustment valve may advantageously be arranged in the integrated embodiment of the housing of the positive displacement pump, for example in a receiving bore or a differently shaped receiving space in a wall of the pump housing.
  • the connections of the adjusting valve can be shaped in such embodiments space and weight saving as holes or other shaped channels in the housing, in particular in said housing wall, the pump housing can therefore simultaneously also form the valve housing or even a part of the valve housing.
  • the actuator is formed as a double-acting actuator piston with two axially opposite, preferably oppositely facing piston surfaces and by means of the adjustment either the one or the other piston surface can be acted upon with a pressurized fluid under pressure, optionally also both piston surfaces simultaneously.
  • the actuator forms an actuating piston which can be pressurized with pressurized fluid, for example a piston which can be pressurized only on one side or preferably a double-acting piston, it is acted upon in preferred embodiments by a pump spring with a spring force, the pump spring acting in the direction of increasing the delivery volume of the pump.
  • the pump spring is so weak that the adjustment dynamics of the pump are not significantly influenced by the pump spring, but exclusively or at least to a significant extent by the adjustment valve. In principle, it is also possible to dispense with a pump spring in such embodiments.
  • a weak pump spring is advantageous, wherein such a pump spring is designed so that it only ensures that in low-speed displacement pump, the maximum pumping speed for this pump speed is promoted. Suffice a pump spring, which exerts on the actuator a spring force corresponding to a fluid pressure of at most 1 bar.
  • the fluid controlled by means of the adjustment valve or regulated to the positive displacement pump for the purpose of adjustment or in the case of an only used as a bypass valve adjusting valve generates the branched off to a reservoir fluid at its flow through the adjusting valve the valve set pressure.
  • a separate Ansclaluss is needed for the generation of the valve actuating pressure.
  • the same inlet, through which the fluid flow passing through the adjusting valve passes into the adjusting valve, also forms the connection for the fluid which generates the valve actuating pressure.
  • valve actuating pressure is generated by means of a plurality of active surfaces, preferably by means of exactly two effective surfaces which differ in size, so that the valve actuating pressure exerts a differential force corresponding to the area difference of the active surfaces on the valve piston.
  • the feature of the differential force is combined with the further feature, after which the fluid also simultaneously generates the valve set pressure during the flow through the adjustment valve.
  • the biasing force of the valve spring can be adjusted, preferably fluidly while the positive displacement pump delivers the fluid.
  • the adjustment valve may have a further piston which is preferably used only to adjust the biasing force and preferably is acted upon by the fluid, which also generates the valve actuating pressure. wherein for the piston for adjusting the biasing force provided a separate connection or preferably a force acting on this adjusting piston force can also be generated by the fluid flowing through.
  • FIG. 1 shows a positive displacement pump in a cross section, in a pump housing 1, a delivery chamber is formed with an inlet 2 on a low pressure side and an outlet 3 on a high pressure side.
  • a first delivery member 4 and a second delivery member 5 are movably arranged in the delivery chamber.
  • the conveyor members 4 and 5 are in a conveying engagement with each other When the conveyor members 4 and 5 are driven, they perform a conveying movement in the conveying engagement through which a fluid, such as lubricating oil or a hydraulic fluid, sucked through the inlet 2 into the delivery chamber and higher pressure through the outlet 3 is displaced.
  • the conveyor member 4 is driven and drives the conveyor member 5 in the conveying engagement.
  • the positive displacement pump of the embodiment is an external gear pump.
  • the conveyor members 4 and 5 are accordingly externally circumferentially toothed conveyor rotors and the conveying engagement a tooth engagement.
  • the conveying members 4 and 5 are rotatably mounted about a respective axis of rotation R 4 and R 5 . In a rotary drive, the sucked fluid from the inlet 2 is transported in each of the conveyor members 4 and 5 formed by the tooth gaps conveyor cells through the region of the so-called loop la and ejected through the outlet 3.
  • R 4 and R 5 measured axial length of the conveying engagement of the conveying members 4 and 5, the engagement length, adjustable.
  • the conveying member 5 is movable relative to the conveying member 4 and the pump housing 1 axially between a position of maximum engagement length and corresponding maximum delivery volume and a position of minimum engagement length and correspondingly minimal delivery volume.
  • FIG. 2 shows the positive displacement pump in a longitudinal section.
  • the conveyor member 4 is secured against rotation on a drive shaft which protrudes from the pump housing 1 and carries a drive wheel for driving the pump.
  • the conveying member 5 is part of an adjusting unit, which comprises an actuator with two adjusting pistons 6 and 7 via the conveying member 5 addition.
  • This adjusting unit 5-7 is as a whole in the pump housing 1 axially movable back and forth to adjust the engagement length can.
  • the conveying member 5 is arranged axially between the adjusting pistons 6 and 7.
  • the actuator 6, 7 supports the conveyor member 5 rotatable about the axis of rotation R 5 .
  • the adjusting unit 5-7 is accommodated in a cylindrical cavity of the pump housing 1.
  • the cavity forms an axial track for the movements of the adjustment, 5-7. Furthermore, it forms on one axial side of the adjusting 5-7 a pressure chamber 8 and on the other side a further pressure chamber 9.
  • the control pistons 6 and 7 separate the two pressure chambers 8 and 9 of unavoidable leakage fluidly apart from each other and also from the delivery chamber.
  • the Pressure chambers 8 and 9 are each printable with a pressurized fluid, in the embodiment with the funded by the positive displacement pump fluid.
  • a pump spring 10 is arranged, the spring force acts on the adjusting unit, 5-7, namely on the actuating piston 7, in the direction of maximum engagement length.
  • the fluid circuit includes a reservoir 11 from which the pump draws the fluid on the low pressure side through the inlet 2 and with higher pressure on the high pressure side through the outlet 3, a connected Supply line 12 and a cooling and cleaning device 13 with a radiator and a filter to the supplied with the fluid unit 14, for example, a Biennkraftmaschine for driving a motor vehicle, promotes. Downstream of the unit 14, the fluid is passed through a conduit 15 back into the reservoir 11.
  • a partial flow 16 of the fluid is diverted and returned via an adjustment valve 20 to the pump.
  • the adjustment valve 20 has an inlet for the partial flow 16, an outlet shorted to the reservoir 11 and two further connections, one of which is connected via a line 18 to the pressure chamber 8 and the other via a line 19 to the pressure chamber 9.
  • the adjustment valve 20 is a multi-way Scllaltventll, in a first switching position, it carries the partial flow 16 in the pressure chamber 8 and connects the pressure chamber 9 with the reservoir II, the pressure chamber 9 thus switches to ambient pressure. In a second switching position, the adjusting valve in FIG.
  • the adjusting valve 20 of the embodiment can take three switching positions, namely the two switch positions mentioned and also a center position in which it separates the pressure chambers 8 and 9 from each other and also from the reservoir 11 and the partial flow 16, so that the respective pressure in the pressure chambers. 8 and 9 is maintained, one of leaks and associated leakage from.
  • a 4/3-way valve was selected for the adjustment valve 20.
  • FIG. 4 shows the adjustment valve 20 as in FIG. 3 as a switching symbol, only in enlarged cooking position. Entered are the four ports of the adjusting valve 20, of which the inlet for the recirculated partial flow 16 with I, the outlet to the reservoir 11 with O, the connection for the pressure chamber 8 with A and the connection for the pressure chamber 9 with B are designated.
  • the adjustment valve 20 is a proportional valve with a constantly acting fluidic valve set pressure P20, namely the pressure of the fluid recirculated in the partial flow 16, and a valve spring 25, which is arranged counter to the valve set pressure P 20 .
  • the adjustment valve 20 comprises as a proportional valve an adjusting device, which adjusts the adjustment valve 20 adapted to the fluid requirement of the unit 14 from one of the switching positions to another.
  • the valve actuating pressure P 20 and the valve spring 25 give the adjusting valve 20 a fail-safe property in the event of failure of the proportional adjusting device.
  • the adjusting device is a magnetic adjustment device, which is connected with a pulse-width-modulated electrical control signal.
  • the control signal is generated by a control device in the form of a square wave signal having a constant upper and a constant lower signal level, for example voltage level, and a specific period t.
  • the pulse width modulation the time duration of the upper signal level, the so-called on-time, and subsequently in the sequence
  • the duration of the lower signal level, the switch-off time can be varied.
  • the magnetic force of the adjusting device changes according to the duty cycle of the actuating signal, ie the ratio of the switch-on time to the period t.
  • the switching position of the adjusting valve 20 results from the force equilibrium of the force of the valve spring 25 and the two counteracting forces, namely the fluidic force generated by the valve actuating pressure P 20 and the Magnetlcraft.
  • the larger the valve actuating pressure P 20 the smaller is the Balance of forces corresponding magnetic force. If the sum of fluidic force and magnetic force exceeds the spring force, the valve piston 22 moves in the direction of the first switching position, and the delivery volume of the positive displacement pump is stopped. If the force of the valve spring 25 predominates, the valve piston 22 moves to the second switching position, and the displacement unit 5-7 moves accordingly in the direction of maximum delivery volume.
  • the switch-on time and the switch-off time are assigned to the first and the second switch position of the adjustment valve 20.
  • the position of the valve piston 22 and, associated therewith, the switching position of the adjustment valve 20 are decoupled from the valve set pressure P 20 .
  • the adjustment valve 20 assumes the first switching position during each switch-on time, in which the fluid of the partial flow 16 is returned to the pressure chamber 8, and during each switch-off time assumes the second switch position, in which the fluid is returned to the pressure chamber 9 ,
  • the flow through the adjustment valve 20 to the respective pressure chamber 8 or 9 can be varied practically continuously in both embodiments because of the significantly shorter period duration t of the actuating signal compared to the relevant time constant of the pump. Accordingly, the pressure in the pressure 8 and the pressure in the pressure chamber 9 can be changed continuously.
  • the adjusting unit can be moved 5-7 along its axial displacement in any axial position and held there.
  • the delivery volume is thus flexibly and precisely continuously adapted to the fluid requirement of the unit 14 between the maximum and the minimum delivery volume.
  • a map in an electronic or optical memory contains for the relevant with regard to the fluid requirements operating conditions of the unit 14 each have a predetermined setpoint for the Fluid supply pressure P 14 or the flow rate V 14 , which requires the unit 14 in each operating condition.
  • These volume flow or pressure setpoints are stored in the map in dependence on physical quantities that characterize the operating conditions to be distinguished with regard to the fluid requirement. Examples of the physical variables are the temperature T, the speed D and the load L called.
  • the unit 14 has a detection device for detecting one or more, the different operating conditions characteristic physical variable (s) on the temperature T, for example, at a critical point of the unit 14, in a cooling of the unit 14 serving cooling fluid or in that of the pump 3 funded fluid can be measured.
  • the speed D can be detected very easily by means of a tachometer and the load L on the accelerator pedal or a throttle position.
  • the control device forms the actuating signal, namely the ratio of the switch-on time to the period t, in accordance with the current setpoint value.
  • a feedback by means of a control variable in this case a measured actual value of the fluid supply pressure P 14 or the volume flow V 14 , is not required as long as the actual eluid demand of the unit 14 corresponds to the desired value.
  • the control on the basis of the desired value can in particular be supplemented by a current control.
  • the current control is used in particular to compensate for changes in resistance of the magnetic adjustment device, as they can take place especially in temperature changes.
  • the current consumption of the adjusting device is detected by a detection device and kept at a specific current value. If, by means of the detection device, a change in the current consumption and accordingly of the electrical resistance of the adjusting device is detected, the duty cycle is changed in such a way that the current consumption again corresponds to the current value before the resistance change.
  • an adjustment valve 20 is also used Control device provided.
  • the control device forms the control signal for the adjustment valve 20 as a function of a desired-actual comparison on the basis of a required for the unit 14 fluid supply pressure P 14 or flow V 14 .
  • the control device has access to a memory in which other setpoint values of the pressure P 14 or volumetric flow V 14 are stored in the form of a characteristic map comparable to the characteristic map previously used for the control.
  • the maps of the pressure setpoints or volume flow setpoints can be stored in physically different memories or in the same memory in different areas.
  • a higher-level control device which may be part of the pressure or volume flow control device or the control device and switches from the controller to a control, if it is determined that the demand of the unit has changed so much that the map of the setpoints does not adequately describe actual demand because demand has increased, for example due to wear.
  • the actual prevailing fluid supply pressure P 14 can be detected, for example, at the most downstream point of consumption of the unit 14 or in the example of the internal combustion engine at the motor gallery and compared with the relevant for the respective operating pressure target value, for example by subtraction of target and actual value.
  • non-feedback pressure or flow control can be further developed to a pressure or flow control with a target / actual comparison of the respective pressure or flow rate setpoint with an actual value to be measured for the comparison.
  • maps for the volume flow V 14 or fluid supply pressure P 14 can be stored in advance, which describe the demand for different times in the life cycle of the unit 14, for example, a map for the first n kilometers of a motor vehicle or n operating hours of the unit 14, the next m mileage of the vehicle or m operating hours of the unit etc.
  • the mileage of the vehicle or a Trodatierer can be converted in such embodiments of the first used map to the next, etc.
  • the controller may also detract from the ability to change the setpoint values of the map in accordance with the state of the engine 14 to better match the adjustment valve 20 with the engine based on the altered map be able to control the respective state of the unit 14 adapted.
  • the change of the setpoint values of the characteristic map or the selection of one of several predetermined Guynfeldelm is advantageously carried out automatically, for example on the basis of the already mentioned mileage or the operating time or a detection of the fluid supply pressure P 14 and comparison with or predetermined in the form of a characteristic pressure setpoint (en Although such a target / actual comparison could be used for a pressure control of the adjustment valve 20, but preferably only for the selection of the pressure or volume flow map to be used or the change in the pressure or flow rate setpoints of a single predetermined map is used for control.
  • FIG. 5 shows in a longitudinal section a modified with respect to the generation of the valve actuating pressure P 20 adjustment valve 20.
  • the valve actuating pressure P 20 is different than in the adjustment of the FIG. 4 not by means of an additional partial flow in the Figures 3 and 4 the partial flow 17, but by means of to be controlled or regulated flow of the partial flow 16.
  • Apart from this modification apply to the adjustment valve 20 of the Figures 3 and 4 made statements for the modified adjustment valve 20 and the comments made for this also for the adjustment valve 20 of the Figures 3 and 4 ,
  • the adjusting valve 20 has a valve housing 21 and a valve piston 22 which can be moved axially back and forth in the valve housing 21 along a central valve axis S.
  • the adjusting device shows a magnet coil 27 and an armature 28 made of soft iron.
  • the solenoid coil 27 is fixedly connected to the valve housing 21 and surrounds the armature 28.
  • the armature 28 is connected to the valve piston 22 axially immovable, so that the valve piston 22 and the armature 28 axial movements such as to execute a unit.
  • the valve piston 22 has a first active surface 2.3 and a second active surface 24 for the valve actuating pressure P 20 .
  • the active surfaces 2, 3 and 24 together axially bound a fluid space 26 and face each other axially.
  • the active surface 23, against which the valve actuating pressure P 20 of the valve spring 25 counteracts, is greater than the effective area 24, wherein in FIG. 5 the circumstances are exaggerated.
  • the difference in size is only slightly, but defined so that the valve actuating pressure P 20 always exerts on the valve piston 22 a differential force corresponding to the size difference of the active surfaces 23 and 24, which counteracts the force of the valve spring 25.
  • valve piston 22 can be made very accurate to the size difference of the active surfaces 23 and 24, and the differential force correspondingly small and the valve spring 25 advantageously softer than in the embodiment of FIG. 4 be. Correspondingly low forces required the adjusting device 27, 28.
  • the adjustment valve 20 is more sensitive overall, and it can be the switching times of the adjustment valve 20 is shortened.
  • the switching position of the adjusting valve 4 in the Figures 3 and 4 corresponds, the port B opens into the fluid chamber 26, and the valve piston 22 separates the fluid chamber 26 and thus the inlet I of the other terminal A. Accordingly, the fluid of the partial flow 16 is returned to the pressure chamber 9, while the pressure chamber 8 via the port A connected to the reservoir 11 and thus connected without pressure.
  • the connection A is connected to the outlet O via a space of the valve housing 21, in which the valve spring 25 is arranged, and to the reservoir 11 via this.
  • the magnetic coil 27 is energized and shifts the armature 28 against the force of the valve spring 25 in the axial direction first in the middle switching position and with a correspondingly long switch-on until the other extreme switching position , the first switch position.
  • the valve piston 22 separates both ports A and B from the fluid chamber 26 into which the inlet I still opens.
  • the valve piston 2.2 assumes such an axial position that the fluid space 26 is in axial overlap with both the inlet I and the port A, while the valve piston 22 in the respective axial position the port B of the Fluid space 26 fluidly separates.
  • the fluid of the partial flow 16 is passed through the fluid space 26 and the port A in the pressure chamber 8, while the pressure chamber 9 via the port B and a passage C of the valve piston 22 to the outlet O and finally connected to the reservoir 11 is.
  • the valve piston 22 is hollow.
  • the passage C is formed in a cylindrical jacket region of the valve piston 22, which adjoins the active surface 24 in the direction of the armature 28 and forms a narrow sealing gap with the surrounding jacket of the valve housing 21, which fluidically displaces the adjusting device 27, 28 from the fluid space 26 separates.
  • the adjusting device 27, 28 with the associated control device switches the adjustment valve 20 over the entire operating range of the unit 14 and controls or regulates the axial position of the adjustment 5-7 and consequently the delivery volume of the positive displacement pump over the entire volume flow range, for the adapted supply of the unit 14 is required.
  • the fluidic valve actuating pressure P 20 and the valve spring 25 serve as a backup application in the event that the adjusting device 27, 28 or the associated control device fails due to a defect, for example due to a cable break or a loose electrical connector.
  • the Verstellverztil 20 is designed so that in the event of failure, the delivery volume of the pump from maximum towards minimum is adjusted only when reaching a fluid supply pressure P 14 , which is greater than a maximum fluid supply pressure P 14 , which is established with proper operation of the adjustment valve 20 ,
  • the valve spring 25 is installed with a biasing force which is greater than a force which exerts a maximum Ventilstelltik P 20 , which can be set with proper function, on the valve piston 22.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Sliding Valves (AREA)
  • Fluid-Driven Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Magnetically Actuated Valves (AREA)
  • Safety Valves (AREA)

Claims (21)

  1. Soupape de réglage pour le réglage du volume de refoulement d'une pompe volumétrique, la soupape de réglage comportant :
    (a) un boîtier de soupape (21),
    (b) un piston de soupape (22) monté de manière mobile dans le boîtier de soupape (21), ayant une surface active (23) pour une pression de réglage de soupape (P20) d'un fluide,
    (c) un ressort de soupape (25) qui contrecarre une force exercée par la pression de réglage de soupape (P20) sur le piston de soupape (22),
    (d) et un dispositif de réglage (27, 28) au moyen duquel le piston de soupape (22) peut être réglé dans la direction de la force exercée par la pression de réglage de soupape (P20),
    (e) dans laquelle le ressort de soupape (25) est pré-chargé,
    caractérisée en ce que le ressort de soupape (25) exerce une force élastique sur le piston de soupape (22) qui est plus grande qu'une force exercée sur le piston de soupape (22) par une pression de réglage de soupape (P20) maximale lorsque le dispositif de réglage (27, 28) fonctionne correctement.
  2. Soupape de réglage selon la revendication précédente et présentant au moins une des caractéristiques suivantes :
    - le dispositif de réglage (27, 28) peut être actionné électriquement,
    - le dispositif de réglage (27, 28) est formé comme un dispositif de réglage magnétique,
    - le dispositif de réglage (27, 28) contrecarre la force du ressort de soupape (25).
  3. Soupape de réglage selon l'une des revendications précédentes et présentant au moins une des caractéristiques suivantes :
    - la soupape de réglage (20) est une soupape proportionnelle,
    - la soupape de réglage (20) est modulée en impulsions, de préférence modulée en largeur d'impulsion, commandée ou régulée,
    - la soupape de réglage (20) est commandée ou régulée par un courant,
    - la soupape de réglage (20) est commandée ou régulée par une tension,
    - la soupape de réglage (20) comporte au moins trois orifices (I, O, A, B), de préférence quatre orifices pour le fluide,
    - la soupape de réglage (20) peut être commutée entre au moins deux positions de commutation, de préférence trois positions de commutation,
    - la soupape de réglage (20) est un distributeur.
  4. Soupape de réglage selon l'une des revendications précédentes, comportant :
    - un dispositif de commande ou de régulation pour la commande ou la régulation d'une pression d'alimentation en fluide (P14) à générer par la pompe volumétrique ou d'un débit volumique (V14) à refouler par la pompe volumétrique,
    - et une valeur de consigne par défaut pour prédéterminer au moins une valeur de consigne pour la pression ou le débit volumique, de préférence une valeur de consigne variable de manière prédéfinie,
    - dans laquelle le dispositif de commande ou de régulation commande ou régule le dispositif de réglage (27, 28) en fonction de la valeur de consigne.
  5. Soupape de réglage selon l'une des revendications précédentes, comportant :
    - un dispositif de régulation pour la régulation d'une pression d'alimentation en fluide (P14) à générer par la pompe volumétrique,
    - une valeur de consigne par défaut pour prédéterminer une valeur de consigne pour la pression d'alimentation en fluide (P14), de préférence une valeur de consigne variable de manière prédéfinie,
    - et un capteur pour la détermination d'une valeur réelle de la pression d'alimentation en fluide (P14),
    - dans laquelle le dispositif de régulation compare la valeur réelle à la valeur de consigne et commande le dispositif de réglage (27, 28) en fonction du résultat de la comparaison.
  6. Soupape de réglage selon une combinaison des deux revendications précédentes, comportant un dispositif de contrôle au moyen duquel la soupape de réglage (20) peut être basculée de la commande de la pression d'alimentation en fluide (P14) ou du débit volumique (V14) vers la régulation de la pression d'alimentation en fluide (P14) ou du débit volumique (V14).
  7. Soupape de réglage selon l'une des revendications précédentes, dans laquelle le piston de soupape (22) comporte une surface active supplémentaire (24) pour la pression de réglage de soupape (P20), et les surfaces actives (23, 24) sont agencées de manière à se contrecarrer l'une et l'autre et sont de taille différente afin de produire une force différentielle qui agit sur le piston de soupape (22) à l'encontre du ressort de soupape (25) et qui correspond à la différence de taille des surfaces actives (23, 24).
  8. Soupape de réglage selon la revendication précédente, dans laquelle les surfaces actives (23, 24) limitent le même espace de fluide (26) et sont dirigées l'une vers l'autre dans la direction de la mobilité du piston de soupape (22).
  9. Soupape de réglage selon la revendication précédente, dans laquelle le piston de soupape (22) est mobile en va-et-vient entre une première position et une seconde position, et dans la première position du piston de soupape (22), une entrée (I) et un orifice (A) pour un fluide sous pression produisant une pression de réglage de soupape (P20) débouchent dans l'espace de fluide (26) et le piston de soupape (22) sépare, dans la seconde position, l'orifice (A) de l'entrée (I) débouchant encore dans l'espace de fluide (26).
  10. Soupape de réglage selon l'une des revendications précédentes, dans laquelle le boîtier de soupape (21) comporte une entrée (I), un premier orifice (A) et un second orifice (B) pour un fluide sous pression, le piston de soupape (22) est mobile en va-et-vient entre une première position et une seconde position, et l'entrée (I) est reliée au premier orifice (A) lorsque le piston de soupape (22) est dans la première position et est séparée du second orifice (B), et est reliée au second orifice (B) lorsque le piston de soupape (22) est dans la seconde position et est séparée du premier orifice (A), afin de guider sélectivement le fluide sous pression jusqu'à la pompe soit par le premier orifice (A) soit par le second orifice (B).
  11. Pompe volumétrique ayant un volume de refoulement réglable, comportant :
    (a) un carter de pompe (1),
    (b) une chambre de refoulement formée dans le carter de pompe (1) avec une entrée (2) pour un fluide sur un côté basse pression et une sortie (3) pour le fluide sur un côté haute pression de la pompe,
    (c) un organe de refoulement (5) mobile dans la chambre de refoulement pour le refoulement du fluide,
    (d) et une soupape de réglage (20) selon l'une des revendications précédentes, agencée dans un écoulement du fluide refoulé par l'organe de refoulement (5) pour régler le volume de refoulement.
  12. Pompe volumétrique selon la revendication précédente, dans laquelle :
    - un organe de réglage (6, 7) est agencé de manière mobile en faisant face à un côté avant de l'organe de refoulement (5) ou en entourant l'organe de refoulement pour régler le volume de refoulement dans le carter de pompe (1),
    - l'organe de réglage (6, 7) peut être soumis, dans la direction de sa mobilité, à une force de réglage qui dépend de la demande d'un ensemble (14) à alimenter en fluide,
    - dans laquelle l'organe de réglage (6, 7) et l'organe de refoulement (5) font partie d'une unité de réglage (5, 6, 7) mobile d'un seul tenant en va-et-vient dans le carter de pompe (1), ou un organe parmi l'organe de réglage et l'organe de refoulement est réglable par rapport à l'autre et au carter de pompe.
  13. Pompe volumétrique selon la revendication précédente et présentant au moins une des caractéristiques suivantes :
    - la pompe est une pompe rotative, et l'organe de refoulement (5) est un rotor de refoulement agencé de façon à pouvoir tourner dans la chambre de refoulement autour d'un axe de rotation (R5),
    - un ressort de pompe (10) est agencé de manière à contrecarrer la force de réglage.
  14. Pompe volumétrique selon l'une des deux revendications précédentes, dans laquelle l'organe de réglage (6, 7) peut être soumis au fluide du côté haute pression de la pompe afin de produire la force de réglage.
  15. Pompe volumétrique selon la revendication précédente, dans laquelle l'organe de réglage (6, 7) forme un piston de réglage à double effet avec une première surface de piston et une seconde surface de piston opposée à la première surface de piston, la première surface de piston peut être soumise à un fluide sous pression, de préférence le fluide du côté haute pression de la pompe, via un premier orifice (A) de la soupape de réglage (20) et la seconde surface de piston peut être soumise à un fluide sous pression, de préférence le fluide du côté haute pression de la pompe, via le second orifice (B) de la soupape de réglage (20), et le piston de soupape (22) est mobile en va-et-vient entre une première position et une seconde position, dans laquelle la soupape de réglage (20) conduit le fluide sous pression, dans la première position du piston de soupape (22), uniquement jusqu'à la première surface de piston et, dans la seconde position, uniquement jusqu'à la seconde surface de piston.
  16. Pompe volumétrique selon l'une des quatre revendications précédentes et présentant au moins une des caractéristiques suivantes :
    - l'organe de réglage (6, 7) est mobile axialement ou transversalement par rapport à l'axe de rotation (R5) conjointement avec l'organe de refoulement (5) ou par rapport à l'organe de refoulement (5),
    - l'organe de refoulement (5) est en prise de refoulement avec un organe de refoulement supplémentaire (4) de la pompe volumétrique,
    - la pompe est une pompe à engrenage extérieur ou à engrenage intérieur,
    - l'organe de réglage (6, 7) comporte un premier piston de réglage (6) et un second piston de réglage (7), et l'organe de refoulement (5) est agencé axialement entre les pistons de réglage (6, 7) et est axialement mobile en va-et-vient avec les pistons de réglage (6, 7) comme une unité de réglage (5, 6, 7) en prise de refoulement par rapport à l'organe de refoulement supplémentaire (4),
    - la pompe est une pompe à ailettes, une pompe à palettes pendulaires ou une pompe à engrenage intérieur, et l'organe de réglage est une bague de réglage mobile transversalement à l'axe de rotation de l'organe de refoulement et entourant l'organe de refoulement.
  17. Pompe volumétrique selon l'une des revendications précédentes, dans laquelle le fluide refoulé par la pompe volumétrique est dévié du côté haute pression de la pompe, de préférence en aval d'un dispositif de nettoyage (13), et peut être redirigé vers la pompe par l'intermédiaire de la soupape de régulation (20) afin d'y produire la force de réglage.
  18. Pompe volumétrique selon la revendication précédente, dans laquelle le fluide redirigé produit la pression de réglage de soupape (P20), de préférence pendant la traversée de la soupape de réglage (20).
  19. Pompe volumétrique selon l'une des revendications précédentes, comportant :
    - un dispositif de détection pour détecter au moins une grandeur physique (T, D, L) qui caractérise la demande de fluide d'un ensemble (14) à alimenter par la pompe,
    - une valeur de consigne pré-établie qui forme une valeur de consigne pour un débit volumique (V14) à refouler par la pompe volumétrique ou une pression d'alimentation en fluide (P14) à produire par la pompe volumétrique, en fonction de la au moins une grandeur physique (T, D, L) détectée,
    - et un dispositif de commande ou de régulation qui commande ou régule le dispositif de réglage (27, 28) de la soupape de réglage (20) en fonction de la valeur de consigne.
  20. Pompe volumétrique selon la revendication précédente, comportant un capteur pour déterminer une valeur réelle du débit volumique (V14) ou de la pression d'alimentation en fluide (P14), dans laquelle le dispositif de régulation forme une grandeur de réglage pour le dispositif de réglage (27, 28) de la soupape de réglage (20) en fonction d'une comparaison de la valeur de consigne et de la valeur réelle.
  21. Pompe volumétrique selon l'une des revendications précédentes et présentant au moins une des caractéristiques suivantes :
    - la pompe est utilisée comme une pompe à huile lubrifiante dans un véhicule pour fournir de l'huile lubrifiante à un moteur à combustion interne (14) ou du liquide hydraulique à une transmission automatique,
    - la pompe est entraînée par le moteur à combustion interne (14).
EP08159994.6A 2007-07-13 2008-07-09 Soupape de réglage pour le réglage du volume d'alimentation d'une pompe volumétrique Not-in-force EP2014919B2 (fr)

Priority Applications (1)

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EP16206318.4A EP3173624B1 (fr) 2007-07-13 2008-07-09 Pompe volumétrique avec soupape de réglage du volume d'alimentation

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200710033146 DE102007033146B4 (de) 2007-07-13 2007-07-13 Verstellventil für die Verstellung des Fördervolumens einer Verdrängerpumpe

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EP16206318.4A Division-Into EP3173624B1 (fr) 2007-07-13 2008-07-09 Pompe volumétrique avec soupape de réglage du volume d'alimentation

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EP2014919A2 EP2014919A2 (fr) 2009-01-14
EP2014919A3 EP2014919A3 (fr) 2010-09-01
EP2014919B1 true EP2014919B1 (fr) 2017-01-04
EP2014919B2 EP2014919B2 (fr) 2020-01-08

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EP08159994.6A Not-in-force EP2014919B2 (fr) 2007-07-13 2008-07-09 Soupape de réglage pour le réglage du volume d'alimentation d'une pompe volumétrique

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EP (2) EP3173624B1 (fr)
JP (1) JP2009019773A (fr)
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HU (1) HUE035833T2 (fr)

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Publication number Priority date Publication date Assignee Title
DE102009060189B4 (de) 2009-12-23 2017-07-13 Schwäbische Hüttenwerke Automotive GmbH Regelvorrichtung für die Verstellung des Fördervolumens einer Pumpe
DE102010038430B4 (de) * 2010-07-26 2012-12-06 Schwäbische Hüttenwerke Automotive GmbH Verdrängerpumpe mit Absaugnut
DE102010039657B4 (de) * 2010-08-23 2017-06-08 Schwäbische Hüttenwerke Automotive GmbH Bypassventil zur Regulierung eines Fluidflusses, zum Beispiel in einer Konstantpumpe
DE102011010835B4 (de) * 2011-02-10 2014-01-30 Audi Ag Verdrängerpumpe
DE102011010834A1 (de) 2011-02-10 2012-08-16 Audi Ag Verstelleinrichtung für einer Verdrängerpumpe
DE102011013756A1 (de) * 2011-03-12 2012-09-13 Volkswagen Aktiengesellschaft Zahnradpumpe mit Verschiebeeinheit zur Einstellung einer Fördermenge
JP5950583B2 (ja) * 2011-03-27 2016-07-13 株式会社山田製作所 ポンプ装置
DE102011055406B4 (de) * 2011-08-05 2016-06-09 Hilite Germany Gmbh Ventileinrichtung für eine Ölversorgungseinrichtung einer Kraftfahrzeug-Brennkraftmaschine
EP2836945A2 (fr) * 2012-04-12 2015-02-18 ITT Manufacturing Enterprises LLC Procédé pour déterminer le débit d'une pompe dans des pompes volumétriques rotatives
US10451471B2 (en) 2012-04-12 2019-10-22 Itt Manufacturing Enterprises Llc Method of determining pump flow in twin screw positive displacement pumps
DE102013211900B4 (de) * 2013-06-24 2025-10-16 Zf Friedrichshafen Ag Kolbenventil und Ventilkolben für ein Kolbenventil
JP2015117638A (ja) * 2013-12-18 2015-06-25 株式会社山田製作所 オイルポンプ装置
DE102016212180A1 (de) 2016-07-05 2018-01-11 Volkswagen Aktiengesellschaft Pumpe, Fluidsystem und Brennkraftmaschine
DE102017200878A1 (de) * 2016-11-14 2018-05-17 Mahle International Gmbh Kraftfahrzeug
DE102017001318B4 (de) 2017-02-11 2022-02-24 Thomas Magnete Gmbh Druckregelventil für eine Verstellpumpe
DE102017206619A1 (de) 2017-04-20 2018-10-25 Bayerische Motoren Werke Aktiengesellschaft Kennfeld geregeltes Steuerventil für eine Schmiermittelpumpe
DE102017109061A1 (de) * 2017-04-27 2018-10-31 Eto Magnetic Gmbh Schieberproportionalventil für die Fördervolumenverstellung einer Verdrängerpumpe, Montageverfahren sowie System
CN110821582A (zh) * 2019-11-18 2020-02-21 福建福清核电有限公司 一种汽轮机润滑油温度调节阀的稳定控制方法

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2326600A1 (fr) * 1975-10-04 1977-04-29 Lucas Industries Ltd Distributeurs pour pompes a course variable
US4600364A (en) 1983-06-20 1986-07-15 Kabushiki Kaisha Komatsu Seisakusho Fluid operated pump displacement control system
DE3905937A1 (de) * 1989-02-25 1990-08-30 Bosch Gmbh Robert Verfahren und vorrichtung zur ansteuerung eines magnetventils
US5645352A (en) * 1993-07-27 1997-07-08 Siemens Aktiengesellschaft Circuit configuration and method for ascertaining the temperature of a current-regulated electrical coil
US5876185A (en) * 1996-11-20 1999-03-02 Caterpillar Inc. Load sensing pump control for a variable displacement pump
EP0908364A2 (fr) * 1997-10-09 1999-04-14 General Motors Corporation Méthode de fonctionnement d' une électrovanne
US6244839B1 (en) * 1997-11-14 2001-06-12 University Of Arkansas Pressure compensated variable displacement internal gear pumps
US6318818B1 (en) * 1998-12-22 2001-11-20 Robert Bosch Gmbh Method for compensating the temperature dependence of an inductive resistance of a valve coil
US20020114708A1 (en) 2000-12-12 2002-08-22 Hunter Douglas G. Variable displacement vane pump with variable target regulator
EP1350930A1 (fr) 2002-04-03 2003-10-08 BorgWarner Inc. Pompe à déplacement variable et dispositif de contrôle
US20050142006A1 (en) 2002-01-12 2005-06-30 Dieter Voigt Device for pressure regulation of hydraulic pumps
US20060104823A1 (en) * 2002-04-03 2006-05-18 Borgwarner Inc. Hydraulic pump with variable flow and variable pressure and electric control

Family Cites Families (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1990750A (en) * 1931-03-02 1935-02-12 Gulf Res & Dev Corp Variable volume pump and hydraulic transmission
DE1917488B2 (de) * 1969-04-05 1977-06-23 Robert Bosch Gmbh, 7000 Stuttgart Steuereinrichtung fuer eine hydromaschine
JPS57131890A (en) * 1981-02-06 1982-08-14 Tokyo Keiki Co Ltd Oil hydraulic controller
DE3109045A1 (de) * 1981-03-10 1982-09-16 Alfred Teves Gmbh, 6000 Frankfurt Regelbare hydraulikpumpe
US4561521A (en) * 1984-12-06 1985-12-31 Ford Motor Company Variable assist power steering system
CN1010794B (zh) * 1986-01-11 1990-12-12 日立建机株式会社 液压泵输入功率控制系统
US4877099A (en) * 1986-09-02 1989-10-31 Ford Motor Company Electronically controlled variable assist power steering system
JPH0544626Y2 (fr) * 1988-05-25 1993-11-12
JPH02161184A (ja) * 1988-12-13 1990-06-21 Daikin Ind Ltd 可変容量形ポンプの制御回路
DE3931962A1 (de) * 1989-09-25 1991-04-04 Rexroth Mannesmann Gmbh Ansteuerelektronik fuer ein elektrisch verstellbares stellglied
US5029513A (en) * 1990-04-27 1991-07-09 Ford Motor Company Variable-orifice, servo-solenoid valve for a variable-assist power steering system
US5392875A (en) * 1991-12-23 1995-02-28 Ford Motor Company Hydraulic reaction variable assist power steering system
JPH0674206A (ja) * 1992-08-26 1994-03-15 Hitachi Constr Mach Co Ltd 油圧モータ容量制御装置
DE4308198C1 (de) * 1993-03-15 1994-07-28 Rexroth Mannesmann Gmbh Drehmomentregelung über Schwenkwinkel bzw. Exzentrizität bei hydrostatischen Maschinen mit axialer und radialer Kolbenanordnung
US5297647A (en) * 1993-03-18 1994-03-29 Ford Motor Company Variable assist power steering gear with hydraulic reaction controls
JPH08177745A (ja) * 1994-12-21 1996-07-12 Hitachi Constr Mach Co Ltd 油圧ポンプ流量制御装置
JPH08210195A (ja) * 1995-02-06 1996-08-20 Nissan Motor Co Ltd ディーゼル機関の排気還流制御装置
CA2219062C (fr) * 1996-12-04 2001-12-25 Siegfried A. Eisenmann Pompe a engrenages a couronne infiniment variable
GB2320955B (en) * 1997-01-03 1999-08-04 Hobourn Automotive Ltd Flow control valve
DE19847132C2 (de) 1998-10-13 2001-05-31 Schwaebische Huettenwerke Gmbh Außenzahnradpumpe mit Fördervolumenbegrenzung
DE19854766A1 (de) * 1998-11-27 2000-05-31 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
JP4117588B2 (ja) * 1999-02-12 2008-07-16 株式会社デンソー 内燃機関の着火時期検出装置
JP2001149921A (ja) * 1999-11-25 2001-06-05 Japan Organo Co Ltd 水処理装置
JP2001271616A (ja) * 2000-01-18 2001-10-05 Unisia Jecs Corp 可変動弁機構の制御装置
GB0001711D0 (en) 2000-01-25 2000-03-15 Btg Int Ltd Data compression having improved compression speed
JP2001271758A (ja) * 2000-03-24 2001-10-05 Komatsu Ltd エンジン回転数センシング機能を有する油圧回路
JP3861594B2 (ja) * 2000-12-15 2006-12-20 ユニシア ジェーケーシー ステアリングシステム株式会社 オイルポンプ
JP2002286151A (ja) * 2001-03-26 2002-10-03 Denso Corp 電磁弁
JP2002350199A (ja) * 2001-05-24 2002-12-04 Samson Co Ltd 演算によって流量を算出する流量算出部を持った通水装置
DE10239558B4 (de) 2002-08-28 2005-03-17 SCHWäBISCHE HüTTENWERKE GMBH Außenzahnradpumpe mit Druckfluidvorladung
DE10324092B4 (de) * 2003-05-27 2010-07-01 Voigt, Dieter, Dipl.-Ing. Regelbare Schmierölpumpe mit einem Fördermengenregler
DE102004002062A1 (de) * 2004-01-15 2005-08-04 Volkswagen Ag Zahnradpumpe mit Fördermengenregelung
JP4202297B2 (ja) * 2004-05-20 2008-12-24 株式会社日立製作所 内燃機関のバルブタイミング制御装置
JP4214965B2 (ja) * 2004-07-22 2009-01-28 株式会社デンソー 蒸発燃料処理装置の漏れ検出装置
US7130721B2 (en) * 2004-10-29 2006-10-31 Caterpillar Inc Electrohydraulic control system
DE102005029086B4 (de) * 2005-06-23 2016-06-16 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Ölpumpe für eine Brennkraftmaschine
US7993111B2 (en) * 2008-01-03 2011-08-09 Ford Global Technologies, Llc Power steering pump flow control

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2326600A1 (fr) * 1975-10-04 1977-04-29 Lucas Industries Ltd Distributeurs pour pompes a course variable
US4600364A (en) 1983-06-20 1986-07-15 Kabushiki Kaisha Komatsu Seisakusho Fluid operated pump displacement control system
DE3905937A1 (de) * 1989-02-25 1990-08-30 Bosch Gmbh Robert Verfahren und vorrichtung zur ansteuerung eines magnetventils
US5645352A (en) * 1993-07-27 1997-07-08 Siemens Aktiengesellschaft Circuit configuration and method for ascertaining the temperature of a current-regulated electrical coil
US5876185A (en) * 1996-11-20 1999-03-02 Caterpillar Inc. Load sensing pump control for a variable displacement pump
EP0908364A2 (fr) * 1997-10-09 1999-04-14 General Motors Corporation Méthode de fonctionnement d' une électrovanne
US6244839B1 (en) * 1997-11-14 2001-06-12 University Of Arkansas Pressure compensated variable displacement internal gear pumps
US6318818B1 (en) * 1998-12-22 2001-11-20 Robert Bosch Gmbh Method for compensating the temperature dependence of an inductive resistance of a valve coil
US20020114708A1 (en) 2000-12-12 2002-08-22 Hunter Douglas G. Variable displacement vane pump with variable target regulator
US20050142006A1 (en) 2002-01-12 2005-06-30 Dieter Voigt Device for pressure regulation of hydraulic pumps
EP1350930A1 (fr) 2002-04-03 2003-10-08 BorgWarner Inc. Pompe à déplacement variable et dispositif de contrôle
US20060104823A1 (en) * 2002-04-03 2006-05-18 Borgwarner Inc. Hydraulic pump with variable flow and variable pressure and electric control

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DE102007033146A1 (de) 2009-01-15
EP3173624A3 (fr) 2017-06-21
US8523535B2 (en) 2013-09-03
JP2009019773A (ja) 2009-01-29
EP2014919B2 (fr) 2020-01-08
US20090041605A1 (en) 2009-02-12
HUE035833T2 (en) 2018-05-28
EP2014919A3 (fr) 2010-09-01
EP3173624A2 (fr) 2017-05-31
DE102007033146B4 (de) 2012-02-02
EP3173624B1 (fr) 2022-01-26
EP2014919A2 (fr) 2009-01-14

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