EP1356208A1 - Systeme de pompage comprenant une pompe hydraulique, destine notamment a un systeme de direction - Google Patents

Systeme de pompage comprenant une pompe hydraulique, destine notamment a un systeme de direction

Info

Publication number
EP1356208A1
EP1356208A1 EP02716707A EP02716707A EP1356208A1 EP 1356208 A1 EP1356208 A1 EP 1356208A1 EP 02716707 A EP02716707 A EP 02716707A EP 02716707 A EP02716707 A EP 02716707A EP 1356208 A1 EP1356208 A1 EP 1356208A1
Authority
EP
European Patent Office
Prior art keywords
pump
cam ring
actuator
pump system
rotor
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.)
Granted
Application number
EP02716707A
Other languages
German (de)
English (en)
Other versions
EP1356208B1 (fr
Inventor
Ulrich Aldinger
Rolf Herkommer
Sven-Uwe Begerow
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch Automotive Steering GmbH
Original Assignee
ZF Lenksysteme GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ZF Lenksysteme GmbH filed Critical ZF Lenksysteme GmbH
Publication of EP1356208A1 publication Critical patent/EP1356208A1/fr
Application granted granted Critical
Publication of EP1356208B1 publication Critical patent/EP1356208B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F04C14/22—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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers
    • 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
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • 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
    • F04C2/3441—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 the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation

Definitions

  • the invention relates to a pump system with a hydraulic pump, in particular for a steering system, according to the preamble of claim 1.
  • a radial piston pump which comprises a drivable rotor with radial bores, in which pump pistons are arranged, which are supported on the inside of a circumferential cam ring, which is mounted eccentrically to the rotor.
  • a plurality of pump pistons which are uniformly distributed over the circumference, are more or less radially pressed into their receiving radial bore in the rotor, depending on the current position of the pump pistons.
  • the pump pistons act on a fluid receiving space, the fluid being sucked into or pushed out of the receiving space depending on the position of the pump pistons. In this way, an approximately constant fluid flow can be promoted.
  • an electrohydraulic pressure regulator which comprises an adjusting piston which adjusts the position of the outer cam ring and which is to be adjusted as a function of a control voltage which is to be supplied to a proportional magnet.
  • the invention is based on the problem of specifying a pump system which can be precisely adjusted and which is distinguished by a good response behavior and at the same time a simple construction.
  • the pump system should expediently have a variable hand and be able to be set to different external load requirements during operation.
  • the pump system comprises, on the one hand, a hydraulic pump for delivering hydraulic fluid to a consumer and, on the other hand, a control and / or regulating unit, in which, depending on measurement signals or other input signals, actuating signals can be generated, which are used by an actuator of the pump to adjust the pump output are feedable.
  • the regulating and control unit advantageously forms a unit which is designed separately from the pump and in which state and operating variables of the consumer, to whom the hydraulic fluid is supplied as the working medium, are supplied as input signals.
  • corresponding variables of a dynamic system can also be taken into account, in which the consumer is embedded and within which the consumer forms a subsystem.
  • control signals are generated from the input signals supplied in accordance with a calculation rule stored as a map or stored as a mathematical relationship, which control signals of the hydraulic pump pe for the current setting of the pump output
  • This pump system is particularly suitable for use in a steering system for steering the wheels in a motor vehicle, the steering system representing the consumer who is supplied with hydraulic fluid by the hydraulic pump, and the motor vehicle representing the superordinate dynamic system, the condition of which the setting of the pump can be taken into account.
  • This pump system offers the advantage of a high degree of variability, since the pump output can be set directly to the requirements of the consumer via the signals from the regulating and control unit, which, particularly when used in steering systems in motor vehicles, leads to parameterizable pumps being implemented in the steering system can be whose performance can be adjusted by state and system variables such as the vehicle speed, the steering angle speed and / or the yaw rate.
  • Another advantage is that in the event that the system is in a stationary or quasi-stationary state, a comparatively low energy consumption can be realized.
  • a variable displacement pump is advantageously used as a pump, which is designed as a vane line pump, a roller cell pump or a radial piston pump.
  • the variable displacement pump has a motor-driven rotor which is rotatably mounted within a cam ring and has radial bores with pump elements which can be displaced radially therein and can be supported with respect to the inside of the cam ring and which act on a fluid receiving space, the relative position between cam ring and rotor via the actuator between a concentric position and an eccentric position is to be adjusted.
  • the pump output is varied via the control signals of the regulating and control unit by adjusting the relative position between the cam ring and the rotor, which is caused by the actuator.
  • the position of the outer cam ring encompassing the rotor is expediently adjusted via an actuator designed as an electric motor.
  • the electromotive adjustment of the outer cam ring offers the advantage that very short response times can be achieved in order to adjust the power output to the current requirement. Response times of up to around 10 ms can be achieved. , _
  • Another advantage is that the electric motor can be controlled very precisely and even small travel ranges, which are associated with high forces, can be implemented. If necessary, it may be expedient to provide a reduction gear between the electric motor and the cam ring in order to be able to achieve the required short actuating distances and high actuating forces even with relatively small electric motors.
  • the pump and the electric motor acting on the cam ring basically form functionally independent units, a higher degree of flexibility is achieved, which in particular This is particularly due to the fact that only the transmission of motion from the rotor of the electric motor to the cam ring must be guaranteed; however, additional support elements on the cam ring are not absolutely necessary.
  • the power supply to the electric motor is also easier to accomplish than the hydraulic supply in hydraulic or electrohydraulic control systems known from the prior art.
  • the rotor of the E lektro otors is advantageously provided with an eccentric disc connected, either directly transmits the necessary actuating movement from the rotor of the electric motor to the cam ring or indirectly via an 'intermediate transfer lever.
  • the intermediate transmission lever is expediently to be displaced translationally, the displacement movement being generated by one end of the transmission lever being acted upon by a cam track on the eccentric disk.
  • the indirect transmission with the interposition of the transmission lever has the advantage that, due to the spatial separation of the pump and the electric motor, there are a multitude of possibilities for arranging the electric motor relative to the pump.
  • eccentric disc it is also possible for the eccentric disc to engage directly on the cam ring, this embodiment being distinguished by a particularly compact size, since there is no need for an intermediate transmission linkage. Friction losses can be minimized.
  • the pump is expediently controlled via a closed control circuit, which has a sensor for measuring an actual variable, which corresponds to the delivery flow or the delivery pressure of the pump, and also a control and regulating unit for comparing the actual variable with a stored one determining target Value and the generation of a value derived from the target-actual comparison for the electric current for the electric motor.
  • the sensor is advantageously designed as a position sensor for determining the position of the cam ring, which can be used as a measure of the delivery pressure or flow, since the amount of deflection of the cam ring relative to a symmetry or center position with respect to the rotor of the pump determines the pump performance.
  • a magnetoresistive sensor for example, can be used as the position sensor for determining the cam ring position, which measures the magnetic field of a permanent magnet, which is arranged on the rotor of the electric motor or a component acted upon by it.
  • the magnetic field of the permanent magnet is changed in relation to the position sensor when the electric motor is actuated, this change in magnetic field being measured and used as a measure of the change in position.
  • FIG. 1 is a schematic representation of a vane pump for conveying a hydraulic fluid from a hydraulic reservoir to a consumer, a cam ring of the radial piston pump influencing the pump performance being adjustable via an electric motor,
  • FIG. 2 shows a schematic illustration of a vane pump with an electric motor with an eccentric disk, the rotational movement of which is converted into a linear, translational transmission movement of a transmission lever
  • 3 shows a representation corresponding to FIG. 2, but with an eccentric disk integrated in the cam ring, which is driven by the rotor of the electric motor
  • Fig. 5 is a schematic diagram of a control loop for adjusting the electric motor.
  • a vane pump 1 which sucks hydraulic fluid from a hydraulic reservoir 3 via a first delivery line 2 and pumps it to a consumer 5 with increased pressure via a second delivery line 4.
  • the consumer 5 is in particular a hydraulically actuated steering system in a motor vehicle.
  • a return line 6 branches off from the delivery line 4, which leads back to the hydraulic reservoir 3 and into which a safety valve 7 is integrated, which is set to the open position when a maximum pressure is exceeded, so that hydraulic fluid flows from the delivery line 4 via the return line 6 back into the hydraulic reservoir 3 can.
  • the safety valve 7 usually only opens at a maximum pressure, which is generally significantly higher than the delivery pressure to be supplied to the consumer 5.
  • the vane pump 1 comprises a rotor 8 which is rotatably mounted in a housing (not shown in more detail) and which is encompassed by a cam ring 9.
  • the rotor 8 is driven by a drive unit, for example an internal combustion engine.
  • the rotor 8 points evenly over its circumference.
  • the displacers 11 are supported on the inside of the cam ring 9.
  • the radial guides 10 communicate with a fluid receiving space for the hydraulic fluid to be conveyed, a relative movement of the radial pistons 11 in the radial bores 10 generating a suction or conveying pressure which sucks the hydraulic fluid out of the hydraulic reservoir 3 and conveys it in the direction of the consumer 5.
  • the pump 1 is designed as a variable displacement pump with a variable pump geometry.
  • the position of the cam ring 9 with respect to the rotor 8 can be adjusted continuously between a concentric position and a maximum eccentric position in which the rotor 8 lies directly against an inside of the cam ring 9.
  • the degree of eccentric deflection of the cam ring 9 with respect to the rotor 8 determines the delivery capacity of the radial piston pump 1.
  • the cam ring 9 is rotatably supported about a bearing point 12.
  • an actuator 13 acts on the cam ring 9; which is designed as an electric motor 14 and whose actuating movement to be transmitted to the cam ring 9 is converted into a pivoting movement in the direction of arrow 15 of the cam ring around its bearing point 12, as a result of which the cam ring is continuously adjusted between its concentric and the maximum eccentric position.
  • the transmission of the actuating movement from the electric motor 14 to the cam ring 9 is expediently carried out via a transmission lever 16 to be moved in a translatory manner, which is acted upon by the rotor of the electric motor and acts tangentially on the cam ring 9.
  • Control signals S ste ⁇ which are generated in a regulating and control unit 18, are supplied to the electric motor 14 for adjustment via signal lines 17.
  • the control signals Ssteii are generated according to a relationship stored in the regulating and control unit 18 as a map or as a calculation formula as a function of input signals S E i n , the state and operating variables of the pump 1, the consumer 5 and, if appropriate, other structural units, in particular an internal combustion engine , represent.
  • the pump geometry is influenced by the change in the relative position between the cam ring and the rotor, which has an effect on the power P to be supplied to the consumer, which has an effect on the relationship
  • V Ge om is a geometry parameter for the pump geometry, which depends on the relative position from the cam ring to the rotor
  • n denotes the speed of the rotor and p the pressure of the hydraulic fluid supplied to the consumer. Since the rotor speed and therefore also the pump power when driven by the internal combustion engine depends on the internal combustion engine speed, a speed-dependent pump control is required to achieve a constant pump output, in which the pump geometry is expediently manipulated.
  • the pump geometry is also adjusted to adapt to the current needs of the consumer by acting on the cam ring via the electric motor.
  • the power P to be supplied to the consumer can also be changed by changing the pressure p to be supplied to the consumer, for example by means of a variably adjustable orifice in the delivery line 4 to the consumer.
  • FIG. 2 shows the radial piston pump 1 in an enlarged, schematic representation.
  • the rotor 19 of the electric motor 14 is connected to an eccentric disc 20 which is driven in rotation by the electric motor.
  • the translationally displaceable transmission lever 16 rests on the peripheral surface of the eccentric disk 20.
  • the peripheral surface of the eccentric disc 20 forms a curved path for the transmission lever 16, so that the current position of the transmission lever is determined by the current rotational position of the eccentric disc 20.
  • the end of the transmission lever 16 opposite the eccentric disc 20 tangentially engages the cam ring 9 on the side radially opposite the bearing point 12 and rotates it in the direction of the arrow 15 about its bearing point 12.
  • a suction port 21, zuzuept- via the hydraulic fluid from the hydraulic reservoir of the pump 1 "ren, and a pressure outlet port 22 via the supply of pressurized hydraulic fluid to the consumer is located.
  • a position sensor 24 shown in FIG. 4 is provided, which is advantageously magnetoresistive and cooperates with a permanent magnet 25 which is expediently arranged on the end face of the eccentric disc 20.
  • the magnetoresistive position sensor 24 is able to measure the magnetic field generated by the permanent magnet 25. Due to the eccentric arrangement of the eccentric disc 20, the position sensor 24 senses a magnetic field which is dependent on the current rotational position of the eccentric disc 20 and from which the rotational position can be deduced. Since the eccentric disc 20 and the cam ring 9 are kinematically coupled, the position of the cam ring 9 can also be inferred from the position of the eccentric disc 20.
  • the position sensor 24 is advantageously held stationary on a circuit board 26 on which additional evaluation components 27 for evaluating the measurement signals of the position sensor 24 are arranged.
  • FIG. 4 also shows that a reduction gear can be provided on the electric motor 14 in order to translate the motor rotation of the electric motor into a smaller rotation, but with a higher torque.
  • FIG. 5 shows a closed control loop, which is implemented in particular in a regulating and control unit 18, for adjusting the electric motor 14 and thus the cam ring of the pump and the delivery rate of the pump.
  • the current actual value of the eccentric disc or the cam ring or a value that corresponds to the position of the cam ring, such as flow rate or delivery pressure, is determined via the position sensor 24.
  • the measured value is used as an input signal S E in a sensor preamplifier
  • the amplified signal is fed to a controller 30, which comprises an analog-digital converter 31 for converting the amplified measurement signal into a digital value, a controller 32 and a pulse width modulator 33.
  • the controller 30 is also assigned a CAN bus 34 for transmitting the vehicle signals to the controller 30 and a calibration memory 35 for calibrating the sensor 24.
  • the function of the various subunits of the controller is controlled by a software control 36
  • the pulse width modulated signal generated in the controller 30 is amplified in an output stage 37 and fed to the electric motor 14 as an actuating signal Ssteii for setting the same.
  • the pump system described above is also suitable for use in transmission systems, for example for lubricating, cooling, switching pumps, or also in other applications in motor vehicles, such as valve controls in internal combustion engines, servo brakes, etc. LIST OF REFERENCE NUMBERS

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Computer Hardware Design (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

La présente invention concerne un système de pompage comprenant une pompe hydraulique (1), présentant un élément de réglage (13) agissant sur la puissance de pompage, qui peut recevoir de la part d'une unité de réglage et de commande (18) des signaux de réglage lui permettant de réaliser le réglage. L'unité de réglage et de commande peut recevoir des signaux d'entrée qui représentent des grandeurs d'état et de fonctionnement d'un récepteur (5) et/ou d'un système dynamique dans lequel est intégré le récepteur. Les signaux de réglage peuvent être produits selon un contexte fonctionnel mis en mémoire dans l'unité de réglage et de commande, en fonction des signaux d'entrée et alimenter l'élément de réglage.
EP02716707A 2001-02-03 2002-02-01 Systeme de pompage comprenant une pompe hydraulique, destine notamment a un systeme de direction Expired - Lifetime EP1356208B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10104851 2001-02-03
DE10104851A DE10104851A1 (de) 2001-02-03 2001-02-03 Pumpsystem mit einer hydraulischen Pumpe, insbesondere für ein Lenksystem
PCT/EP2002/001023 WO2002063170A1 (fr) 2001-02-03 2002-02-01 Systeme de pompage comprenant une pompe hydraulique, destine notamment a un systeme de direction

Publications (2)

Publication Number Publication Date
EP1356208A1 true EP1356208A1 (fr) 2003-10-29
EP1356208B1 EP1356208B1 (fr) 2004-09-15

Family

ID=7672712

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02716707A Expired - Lifetime EP1356208B1 (fr) 2001-02-03 2002-02-01 Systeme de pompage comprenant une pompe hydraulique, destine notamment a un systeme de direction

Country Status (6)

Country Link
US (1) US20040096334A1 (fr)
EP (1) EP1356208B1 (fr)
JP (1) JP2004522909A (fr)
DE (2) DE10104851A1 (fr)
ES (1) ES2229111T3 (fr)
WO (1) WO2002063170A1 (fr)

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Title
See references of WO02063170A1 *

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ES2229111T3 (es) 2005-04-16
WO2002063170A1 (fr) 2002-08-15
EP1356208B1 (fr) 2004-09-15
DE50201013D1 (de) 2004-10-21
DE10104851A1 (de) 2002-08-22
JP2004522909A (ja) 2004-07-29
US20040096334A1 (en) 2004-05-20

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