WO2015193170A1 - Dispositif de pompage - Google Patents

Dispositif de pompage Download PDF

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Publication number
WO2015193170A1
WO2015193170A1 PCT/EP2015/063059 EP2015063059W WO2015193170A1 WO 2015193170 A1 WO2015193170 A1 WO 2015193170A1 EP 2015063059 W EP2015063059 W EP 2015063059W WO 2015193170 A1 WO2015193170 A1 WO 2015193170A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
pump
kidney
consumer
low
Prior art date
Application number
PCT/EP2015/063059
Other languages
German (de)
English (en)
Inventor
Christian ROLL
Ewgeni Schleining
Original Assignee
Magna Powertrain Bad Homburg 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 Magna Powertrain Bad Homburg GmbH filed Critical Magna Powertrain Bad Homburg GmbH
Publication of WO2015193170A1 publication Critical patent/WO2015193170A1/fr

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
    • F04C14/02—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for several machines or pumps connected in series or in parallel
    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • 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
    • F04C2/32—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 both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members
    • F04C2/332—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 both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member

Definitions

  • the present invention relates to a pump device for a motor vehicle and a method for operating a pump device.
  • Pumps find use in automotive and engine technology in many embodiments.
  • vane pumps In the field of automotive engineering, pumps, in particular vane pumps, are used to supply hydraulic systems.
  • Such vane pumps generally consist of a rotor with radially movable wings, a lifting ring with a stroke contour that defines the pump chamber, a pressure and side plate and a housing with housing cover.
  • the pressure and side plate are kidney-shaped recesses, the so-called suction and / or pressure kidneys. Fluid is supplied from a fluid tank to the pump chamber via the suction kidney. Via the pressure kidney, the fluid leaves the pump room.
  • the pressure in the suction kidneys is called the suction pressure and is in the range of the ambient atmospheric pressure (1 bar).
  • the pressure on the pressure kidneys is called the system pressure and represents the pressure required by the consumer.
  • channels are incorporated in the pressure plate and side plate, through which the system pressure can be applied to the lower wing surfaces (undercut groove).
  • the document WO 03/056180 A1 describes a double-stroke vane-cell pump, the pump having a first pump half and a second pump.
  • half of the pen contains.
  • the first pump half is formed from a first suction region and a first pressure region;
  • the second pump half is formed from a second suction region and a second pressure region.
  • Each pump half has a suction kidney and a pressure kidney.
  • the underwing grooves of the pump are divided in two, and each pump half has one of the two undercut grooves. Due to this construction, both pump halves can be used as two separately available feed pumps.
  • a pump as described above is typically operated by an internal combustion engine. If one uses an electric motor for this, in the case of the two load cases
  • the electric motor can only be operated with good efficiency in one of the two load cases, so that the power required by the overall unit, that is pump and electric motor, is low.
  • a pump device for a motor vehicle comprising a pump, wherein the pump has a first flow and a second tide, the first trough having a first suction kidney and the second trough having a second suction kidney, the first suction kidney and the second suction kidney being connectable via a suction line to a fluid reservoir, the first trough having a first pressure kidney and the second teat Tide having a second pressure kidney, wherein the first pressure kidney is connected via a first pressure line to a low pressure consumer and the second pressure kidney is connected via a second pressure line with a changeover valve, wherein the changeover valve, the second pressure line optionally with the low pressure consumer or with a High pressure consumer connects.
  • the pumping device has a double-flow pump, that is, the pump has two separate pump halves, with one half of the pump being called a trough.
  • a first tide has a first suction area, a first suction area, a first pressure area, a first trough
  • the pump of the pumping device thus has a first and a second tide, wherein a fluid from a fluid reservoir to the high-pressure consumer or the low-pressure consumer can be conveyed via the second tide independently of the first tide, depending on the circuit of the switching valve. This makes it possible to supply a high-pressure consumer only on the second flood of the pump to a cooling fluid promote, so that a pump drive can be operated with a good efficiency.
  • the low-pressure consumer is connected via the first pressure line directly to the first flood.
  • the fluid from the fluid reservoir to the low-pressure consumer can be permanently conveyed via the first flow and the first pressure line.
  • the pump of the pumping device can be operated via an internal combustion engine, but preferably via an electric motor.
  • the pump of the pumping device is a gear pump or pendulum slide pump or a vane pump.
  • the second tide is the same size as the first tide of the pump or the second trough smaller than the first tide. If the second tide is smaller than the first tide, the pump room of the second tide is reduced.
  • the speed of the pump is further increased to deliver fluid to the high pressure consumer. This in turn has an advantageous effect on the efficiency of the electric motor and subsequently on the power required by the total unit.
  • the object of the invention is also achieved by a method for operating the pumping device according to the invention, wherein to switch to a low-pressure region via the changeover valve, the second pressure line is connected to the low-pressure consumer and the second pressure line is connected to the high pressure consumer for switching to a high pressure region via the changeover valve.
  • the second flood can additionally be used to convey the fluid from the fluid reservoir to the low-pressure consumer - in this case, the second pressure line is connected to the low-pressure consumer via the change-over valve.
  • a promotion of the fluid from the fluid reservoir to the high pressure consumer takes place in a high-pressure operation via the connection of the second pressure line via the switching valve with the high-pressure consumer.
  • the high-pressure consumer is thus supplied only via the second flood of the pump with the fluid from the fluid reservoir.
  • the low-pressure consumer is permanently supplied with the fluid from the fluid reservoir via the first flood and, by switching over the switching valve and resulting in connecting the second pressure line to the low-pressure consumer, can additionally use the second fluid with the fluid from the fluid reservoir be supplied.
  • the fluid-conveying pump chamber is reduced in size - only the second flow conveys the fluid from the fluid reservoir to the high-pressure consumer.
  • the reduction the fluid-conveying pumping space causes the torque to drop and the pump speed to be increased to deliver the same amount of fluid from the fluid reservoir over only the second flow.
  • Increasing the speed increases the power consumption of the pump.
  • the electric motor can be operated in a better efficiency, so that the power required by the total unit decreases. This makes it possible to use a smaller electric motor and save costs, as well as weight.
  • the first flood promotes when switching to the high pressure area, that is, when connecting the second flood via the second pressure line and the switching valve with the high-pressure consumer, the fluid from the fluid reservoir with low pressure and thus can without interruption a low-pressure consumer with the Supply fluid from the fluid reservoir.
  • the first flood delivers fluid without interruption, that is, independent of the switching of the switching valve, in the low pressure range.
  • Fig. 1 shows a schematic circuit diagram of the pumping device according to the invention
  • Fig. 2 shows a diagram "speed vs. torque"
  • FIG. 1 shows a schematic circuit diagram of the pump device 1 according to the invention.
  • the pump device 1 has the pump with the first flow 2 and the second flow 3.
  • the first tide 2 is composed of the first suction kidney, the first suction region, the first pressure region, the first pressure kidney and the first underfloor groove.
  • the second flow 3 is composed of the second suction kidney, the second suction region, the second pressure region, the second pressure kidney and the second underfloor groove.
  • the first flood 2 and the second flood 3 are thus not connected to it and can be operated independently of one another as a delivery pump. For this reason, in FIG. 1 the first flood 2 and the second flood 3 symbolically represented by the single-pump symbols 2 and 3.
  • Pumping device 1 is sucked via a suction line 4, the fluid from the fluid id-reservoir 5 in the first suction region of the first flood 2.
  • the fluid is brought from the fluid reservoir 5 to the pressure required for the low-pressure consumer 7 and fed via the first pressure kidney of the first pressure line 6.
  • fluid is sucked from the fluid reservoir 5 into the second suction region of the second flow 3 via a suction line 4.
  • the fluid is removed from the fluid Reservoir 5, depending on the circuit of the changeover valve 9, brought to the pressure required for the low-pressure consumer 7 or high pressure consumer 10 and fed via the second pressure kidney of the second pressure line 8.
  • a first pressure line 6 leads directly to a low-pressure consumer 7, from the second tide 3
  • a second pressure line 8 leads to a switching valve 9 that the second pressure line 8 either with the low-pressure consumer 7, or with the high pressure - Consumer 10 connects.
  • the pump device 1 includes a first flow 2 and a second flow 3 via the same time by connecting the high-pressure consumer 10 with the second flow 3 via the second pressure line 8 and the switching valve 9, both the low-pressure consumer 7 with the fluid the
  • Fluid reservoir 5, as well as the high pressure consumer 10 can be supplied with the fluid from the fluid reservoir 5.
  • the first pressure line 6 is connected to the first flood 2 and promotes, even if the second flood 3 is connected via the second pressure line 8 and the switching valve 9 to the high pressure consumer 10, the fluid from the fluid reservoir 5 with low pressure to the Low pressure consumer 7.
  • the fluid for the high pressure consumer 10 is thus promoted only from the second tide 3.
  • the low-pressure consumer 7 is permanently supplied with the fluid from the first flood 2 and can be supplied by switching the changeover valve 9 and connecting the second pressure line 8 with the low-pressure consumer 7 in addition to the second flood 2 with the fluid.
  • the pump of the pump device 1 is via an internal combustion engine, but preferably via an electric motor 1 1 operable.
  • the pump of the pumping device 1 is a gear pump or pendulum slide pump or a vane pump.
  • the second flow 3 of the pump is the same size as the first flow 2 of the pump, but preferably the second flow 3 is smaller than the first flow 2.
  • FIG. 2 shows the diagram "Speed Yl Vs. Torque X "and shows the influence of the pump device 1 according to the invention on the load case” low pressure consumer “12 and the load case” high pressure consumer “13.
  • the dashed line shows the course of the motor efficiency Y2 of an exemplary electric motor 1 1.
  • the chain of effects according to the invention in the load case "high pressure consumer” 13 is as follows: by connecting the second flow 3 via the second pressure line 8 and via the changeover valve 9 with the high pressure pressure-reducing device 10 there is a reduction of the fluid-conveying pump space of the second flow 3 - only the second flow 3 of the pump of the pump device 1 is used to deliver the fluid from the fluid reservoir 5 at high pressure via the second pressure line 8 to the high pressure pressure consumer 10 to promote.
  • the reduction of the fluid-conveying pump chamber causes the torque X decreases and the pump of the pumping device 1 must be operated at a higher speed Yl to promote the same flow rate with only the second flood 3.
  • the diagram in FIG. 2 thus shows that the described increase in the rotational speed Y1 advantageously influences an operation of the pump of the pump device 1 with an electric motor 1 1 - the electric motor 11 operates with higher engine efficiency Y 2.
  • a reduction of the pump space of the second flood 3 with respect to the first flood 2 also causes the pump in the load case "high pressure consumer" 13 must be operated at a higher speed Yl and thus improve the motor efficiency Y2 of the electric motor 1 1st LIST OF REFERENCE NUMBERS

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un dispositif de pompage (1) destiné à un véhicule automobile et comprenant une pompe. La pompe comprend un premier écoulement (2) et un deuxième écoulement (3), le premier écoulement (2) présente un premier orifice d'aspiration et le deuxième écoulement (3) présente un deuxième orifice d'aspiration, le premier orifice d'aspiration et le deuxième orifice d'aspiration peuvent être raccordés à un réservoir de fluide (5) par une conduite d'aspiration (4), le premier écoulement (2) présente un premier orifice de pression et le deuxième écoulement (3) présente un deuxième orifice de pression, le premier orifice de pression est raccordé à un consommateur basse pression (7) par l'intermédiaire d'une première conduite de pression (6) et le deuxième orifice de pression est raccordé à une soupape d'inversion (9) par l'intermédiaire d'une deuxième conduite de pression (8), et la soupape d'inversion (9) raccorde sélectivement la deuxième conduite de pression (8) au consommateur basse pression (7) ou à un consommateur haute pression (10).
PCT/EP2015/063059 2014-06-16 2015-06-11 Dispositif de pompage WO2015193170A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014211457.8 2014-06-16
DE102014211457 2014-06-16

Publications (1)

Publication Number Publication Date
WO2015193170A1 true WO2015193170A1 (fr) 2015-12-23

Family

ID=53433182

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2015/063059 WO2015193170A1 (fr) 2014-06-16 2015-06-11 Dispositif de pompage

Country Status (1)

Country Link
WO (1) WO2015193170A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018200225B3 (de) 2018-01-09 2019-03-07 Magna Powertrain Bad Homburg GmbH Pumpenanordnung für ein Fahrzeug, sowie Steuerung für eine Pumpenanordnung und Verfahren

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1581510A (en) * 1977-08-19 1980-12-17 Garrett Corp Fluid pumping system
DE3210759A1 (de) * 1981-09-17 1983-10-06 Walter Schopf Pumpenkombination mit mengenreguliereinrichtung
EP0385211A1 (fr) * 1989-03-03 1990-09-05 Vickers Incorporated Machine hydraulique rotative
US20020192080A1 (en) * 2000-01-21 2002-12-19 Rytlewski Thomas C. Dual discharge hydraulic pump and system therefor
WO2003056180A1 (fr) 2001-12-27 2003-07-10 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Pompe
US7946402B2 (en) * 2005-03-31 2011-05-24 Gkn Driveline International Gmbh Motor vehicle hydraulic pump

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1581510A (en) * 1977-08-19 1980-12-17 Garrett Corp Fluid pumping system
DE3210759A1 (de) * 1981-09-17 1983-10-06 Walter Schopf Pumpenkombination mit mengenreguliereinrichtung
EP0385211A1 (fr) * 1989-03-03 1990-09-05 Vickers Incorporated Machine hydraulique rotative
US20020192080A1 (en) * 2000-01-21 2002-12-19 Rytlewski Thomas C. Dual discharge hydraulic pump and system therefor
WO2003056180A1 (fr) 2001-12-27 2003-07-10 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Pompe
US7946402B2 (en) * 2005-03-31 2011-05-24 Gkn Driveline International Gmbh Motor vehicle hydraulic pump

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018200225B3 (de) 2018-01-09 2019-03-07 Magna Powertrain Bad Homburg GmbH Pumpenanordnung für ein Fahrzeug, sowie Steuerung für eine Pumpenanordnung und Verfahren

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