EP2179181B1 - Getriebepumpe und verfahren zur flüssigkeitsausgabe mittels einer solchen pumpe - Google Patents

Getriebepumpe und verfahren zur flüssigkeitsausgabe mittels einer solchen pumpe Download PDF

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Publication number
EP2179181B1
EP2179181B1 EP20080828028 EP08828028A EP2179181B1 EP 2179181 B1 EP2179181 B1 EP 2179181B1 EP 20080828028 EP20080828028 EP 20080828028 EP 08828028 A EP08828028 A EP 08828028A EP 2179181 B1 EP2179181 B1 EP 2179181B1
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EP
European Patent Office
Prior art keywords
fluid
circuit
gear pump
pump
circuits
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Not-in-force
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EP20080828028
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English (en)
French (fr)
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EP2179181A2 (de
Inventor
Jean-Claude Heitzler
Christian Muller
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Cooltech Applications SAS
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Cooltech Applications SAS
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Publication of EP2179181A2 publication Critical patent/EP2179181A2/de
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Publication of EP2179181B1 publication Critical patent/EP2179181B1/de
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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
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • 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
    • F04C14/10—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • 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
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • 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
    • Y10T137/0318—Processes

Definitions

  • the present invention relates to a gear pump comprising a pump body in which are housed at least two toothed wheels, of parallel axes, engaged and delimiting on one side of the intermeshed zone a suction chamber and on the other side a thrust chamber of the intermeshed zone, said body having at least one fluid inlet connected to at least one fluid supply circuit and communicating with said suction chamber, and at least one fluid outlet connected thereto; at least one fluid utilization circuit and communicating with said discharge chamber.
  • the invention also relates to a fluid distribution method in at least two use circuits from at least one supply circuit.
  • the gear pump technology is well known and recommended in the case where a high precision of the quantity of fluid dispensed and / or a high pressure is needed.
  • This technology as well as the other known types of pump deliver a fluid in a single circuit of use, and comprise for this purpose, an inlet and an outlet port.
  • To supply a fluid in two separate use circuits either two separate pumps or a double-body pump are used which corresponds to two pumps in the same pump body.
  • no known pump is designed to circulate a fluid alternately in two separate use circuits.
  • the switches commonly used are three-way valves specifically controlled by a source of energy external to the thermal generator, which can be electric or pneumatic. The presence of these switches limits the frequency of the alternating circulation cycle of the fluid.
  • the present invention aims to solve this problem by proposing a new generation of gear pump capable of distributing a fluid alternately in two separate use circuits without switch.
  • the invention relates to a gear pump of the type indicated in the preamble, characterized in that said pump comprises at least two fluid outlet orifices connected to at least two circuits for using the fluid, these outlet orifices. communicating with said discharge chamber by means of integrated switching means and arranged to distribute this fluid alternately in said utilization circuits according to a predetermined switching cycle, which may be substantially equal to the rotation of the gear wheels during, plus a half turn.
  • the switching means comprise a plate mounted in the body in plane support on the gears, the plate comprising at least two distribution circuits and the gears each comprising at least one buffer channel, said buffer channels being arranged to put in communication alternately said distribution circuits with the discharge chamber and the outlet orifices during the rotation of the gears.
  • the distribution circuits and the buffer channels may be formed by recesses formed respectively in the plate and the toothed wheels.
  • the buffer channels advantageously comprise at least one angular sector centered on the axis of rotation of each toothed wheel, and offset with respect to each other by the value of said angular sector.
  • the angular sectors are at most equal to 180 ° and are offset from each other by 180 °.
  • each buffer channel comprises an upstream point coincident with the axis of rotation of the toothed wheel and a downstream point included in the angular sector.
  • each distribution circuit comprises an upstream channel arranged to put the discharge chamber in communication with the upstream point of the corresponding buffer channel, and a downstream channel arranged to put in communication the downstream point of the buffer channel. with the corresponding output port, when the input of said downstream channel is located opposite said buffer channel.
  • the output of the upstream channel and the input of the downstream channel are advantageously separated by an interval substantially equal to the radius of the angular sector of the buffer channel, and the upstream channels of the distribution circuit communicate via the same input connected to the discharge chamber.
  • the invention relates to a method of fluid distribution of the type indicated in the preamble, characterized in that at least one gear pump as defined above is used, this pump comprising integrated switching means and arranged to distribute said fluid alternately in the use circuits according to a predetermined switching cycle.
  • the gear pump 1 according to the invention comprises a pump body 2 in which are housed two identical gear wheels 3 of axes
  • At least one of the gears 3 is rotated by an actuator (not shown), such as an electric motor or the like, the other gear 3 being driven automatically by the drive gear at the same speed. Since gear pumps are known, the description of the pump itself will not be detailed.
  • This pump 1 comprises a fluid inlet orifice 4 intended to be connected to a supply circuit (not shown), this inlet orifice 4 being provided in the body 2 and opening into the suction chamber B.
  • the pump 1 of the invention comprises two fluid outlet ports 5, 6 intended to be connected to two use circuits (not shown). These outlet orifices 5, 6 are provided in the body 2 and communicate with the discharge chamber C via integrated switching means 7, arranged to distribute the fluid leaving the pump 1 alternately in said use circuits according to a predetermined switching cycle.
  • the number of inlet ports 4 may be greater than one, if the pump 1 is connected to several supply circuits supplying different fluids alternately or a mixture of several fluids.
  • the number of outlets 5, 6 may be greater than two, if the pump 1 is connected to several parallel use circuits.
  • the number of gears 3 may be greater than two, meshed with each other to form a gear train coupled to a single actuator, to distribute one or more fluids in parallel circuits.
  • This pump 1 can also be declined in stage pump or double body.
  • the example of pump 1 illustrated in figures 1 and 2 is not limiting
  • the switching means 7 comprise a plate 70 of the fluid mounted in the body 2 in plane support on the gears 3 and under the pump cover (not shown).
  • the connection between the plate 70 and the body 2 is sealed by any type of sealing means (not shown).
  • This plate 70 has distribution circuits 50, 60, the number of which is equal to that of the outlet orifices 5, 6, namely two distribution circuits, in the example shown.
  • These distribution circuits 50, 60 are respectively in communication on the one hand with the discharge chamber C through an orifice 71 provided in the body 2 and on the other hand with the outlet orifices 5, 6.
  • the distribution circuits are made by through recesses obtained by machining, molding or the like, and require to be closed on the opposite side to the toothed wheels 3 by a sealed cover (not shown). They can also be made by blind hollows.
  • the plate 70 forms the cover of the pump body 2.
  • the switching means 7 also comprise buffer channels 30, 40 which are, in the example shown, the number of two buffer channels 30, 40 respectively provided in the toothed wheels 3, and more particularly in the face of these gears 3 in correspondence with the plate 70, so that they can communicate with the distribution circuits 50, 60, when the plate 70 is mounted on the body 2. They are made by blind recesses obtained by machining, molding or the like.
  • Each buffer channel 30, 40 begins at an upstream point 31, 41 coincides with the axis of rotation A of the toothed wheel 3, continues with a straight sector 32, 42 defining a radius R, extended by an angular sector 33, 43 of radius R centered on the axis of rotation A, and ends at a downstream point 34, 44.
  • the angular sector 33, 43 of the buffer channels 30, 40 extends over approximately 180 °, so that, on a complete revolution performed by the gears 3, the buffer channels 30, 40 open and close the distribution circuits 50, 60 per cycle of a half-turn.
  • these two buffer channels 30, 40 are offset by 180 °, so that they work alternately on each cycle.
  • the buffer channels 30, 40 and the angular value of the sector 33, 44 may vary depending on the fluid flow rate to be dispensed with each cycle.
  • the cooperation between the distribution circuits 50, 60 provided in the stationary plate 70 and the buffer channels 30, 40 provided in the rotating gears 3 makes it possible to create the switching function between two fluid circuits, this function being totally integrated in the pump. 1.
  • the distribution circuits 50, 60 provided in the plate 70 comprise an upstream channel 51, 61, whose fluid inlets 52, 62 are coincidental and in correspondence with the orifice 71 supplied by the delivery chamber C, and whose outputs fluid 53, 63 are in correspondence with the upstream point 31, 41 of the buffer channel 30, 40 which corresponds to them.
  • the upstream channels 51, 61 and the buffer channels 30, 40 are always supplied with fluid. They also comprise a downstream channel 54, 64, whose fluid inlets 55, 65 are in correspondence with the downstream point 34, 44 of the buffer channel 30, 40 which corresponds to them on a half turn of the toothed wheels 3, and whose output fluid 56, 66 is in correspondence with the outlet port 50, 60 corresponding thereto.
  • This downstream channel 54, 64 is therefore supplied with fluid on a half turn of the toothed wheels 3 and not supplied with fluid on the next half turn.
  • the output 53, 63 of the upstream channels 51, 61 and the input 55, 65 of the downstream channels 54, 64 are separated by an interval substantially equal to the radius of the angular sector 33, 43 of the buffer channels 30, 40
  • this mode of distribution alternated with each half-turn of the toothed wheels 3, without overlapping period can be modified as desired by changing the design of the channels 30, 40, 54, 64, to obtain an alternating distribution, on portions 3 different gears, with or without recovery period, in two or more circuits of use.
  • the Figure 2A illustrates the distribution of the fluid in a first distribution circuit (not shown) connected to one of the outlet orifices 5.
  • the incoming fluid Fe arrives in the suction chamber B of the pump 1 via the inlet orifice 4, and spring of the discharge chamber C through the orifice 71. It then enters the upstream channel 51 of the distribution circuit 50 by the fluid inlet 52 springing through the fluid outlet 53 to enter the upstream point 31 of the buffer channel 30.
  • the fluid fills the buffer channel 30 until the downstream point 34 of its angular sector 33 is in correspondence with the fluid inlet 55 of the downstream channel 54, allowing the evacuation of the outgoing fluid Fs through the outlet of fluid 56, then the outlet orifice 5 towards a first distribution circuit.
  • the Figure 2B illustrates the distribution of the fluid in a second distribution circuit (not shown) connected to one of the outlet orifices 6.
  • the incoming fluid Fe arrives in the suction chamber B of the pump 1 via the inlet orifice 4, and spring from the discharge chamber C through the orifice 71. It then enters the upstream channel 61 of the distribution circuit 60 via the fluid inlet 62 that exits through the fluid outlet 63 to enter the upstream point 41 of the buffer channel 40.
  • the fluid fills the buffer channel 40 until the downstream point 44 of its angular sector 43 is in correspondence with the fluid inlet 65 of the downstream channel 64, allowing the evacuation of the outgoing fluid Fs through the outlet of fluid 66, then the outlet port 6 towards a second distribution circuit.
  • the fluid leaving the discharge chamber C of the pump 1 splits in two at the fluid inlet 52, 62 and is distributed simultaneously in the upstream channels 51,61 of the distribution circuits 50, 60 , then in the buffer channels 30, 40, so that the pump 1 remains primed and that the flow of the fluid Fs outlet is equal to the flow rate of the incoming fluid Fe divided by 2.
  • the geometry and dimensions of the distribution circuits 50, 60 and buffer channels 30, 40 are determined so that the volume of fluid that they can contain corresponds substantially to volume of fluid conveyed by the pump 1 during a complete revolution of the toothed wheels 3.
  • the gear pump 1 according to the invention can be made by any known manufacturing process and in any material, suitable and selected according to the applications, the nature of the fluid to be conveyed, the dimensions of the pump and fluid flow rates. Since the switching means 7 require a sliding contact between the fixed plate 70 and the rotating gears 3 to ensure the circulation of the fluid and the circuit switching with a minimum of leaks, it is possible to choose to make one of the parts in a material having a very low coefficient of friction such as Teflon®.
  • This new gear pump technology 1 makes it possible to envisage various fluid distribution methods in which it is necessary to distribute or circulate a fluid alternately in at least two use circuits from at least one circuit. 'food.
  • This specific need is encountered in particular in thermal generators, used for heating, air conditioning, tempering, etc. in any technical field, and for which it is necessary to recover the calories and the frigories by at least one coolant circulating in closed loop through at least one hot circuit and a cold circuit, these circuits being respectively associated with a heat exchanger hot and to a cold heat exchanger.
  • FIGS. 3 to 6 illustrate schematically two examples of a fluid distribution method in hot and cold circuits of a thermal generator magnetocaloric material. These examples can of course be extended to any other type of heat generator.
  • AMR Active Refrigerator or Magnetic Regenerator abbreviation
  • CM magnetic element CM arranged to produce a magnetic field variation.
  • the active elements AMR1 and AMR2 are each traversed by two separate fluid circuits, one corresponding to the hot circuit and the other corresponding to the cold circuit, in which a hot heat transfer fluid and a cold heat transfer fluid circulate respectively.
  • the hot fluid is circulated in the hot circuit by a first gear pump 1 as defined above, referenced Pc
  • the cold fluid is circulated in the cold circuit by a second gear pump 1, referenced Pf.
  • Each circuit comprises a heat exchanger Ec, Ef, whose output is connected to the inlet port 4 of the pump Pc, Pf corresponding.
  • each pump Pc, Pf are each connected to an active element AMR1 and AMR2, and the outputs of these active elements AMR1 and AMR2 corresponding to the same circuit are connected to each other and to the input of the exchanger Ec, Ef corresponding.
  • the magnetic element CM is opposite the active element AMR1 which heats up in the presence of the magnetic field or an increase in the value of this field.
  • the heat transfer fluid is circulated C1 hot to recover the calories produced, while cold coolant F1 is stopped.
  • a first switching cycle of the pump Pc is used to dispense the fluid C1 via its outlet orifice 5.
  • This fluid C1 enters the active element AMR1 and leaves it at a higher temperature C1 + to enter the exchanger Ec which uses Calories. It comes out at a lower temperature C1 and returns to the pump Pc.
  • the other active element AMR2 that is not subject to the magnetic field or is subjected to a lower field value, cools down.
  • the cold heat transfer fluid F2 is circulated to recover the frigories produced, while the cool heat transfer fluid C2 is stopped.
  • a first cycle of switching of the pump Pf is used to distribute the fluid F2 through its outlet orifice 6.
  • This fluid F2 enters the active element ANIR2 and leaves at a lower temperature F2- to enter the exchanger Ef who uses the frigories. It comes out at a higher temperature F2 and returns to the pump Pf.
  • the magnetic element CM has moved and is opposite the active element AMR2 which heats up in the presence of the magnetic field or an increase in the value of this field.
  • the hot coolant C2 is circulated to recover the calories produced, while the cold heat transfer fluid F2 is stopped.
  • a second switching cycle of the pump Pc is used to dispense the fluid C2 through its outlet orifice 6: This fluid C2 enters the active element AMR2 and leaves it at a higher temperature C2 + to enter the exchanger Ec which uses Calories. It comes out at a lower temperature C2 and returns to the pump Pc.
  • the other active element AMR1 that is no longer subject to the magnetic field or is subjected to a lower field value, cools.
  • the cold coolant F1 is circulated to recover the frigories produced, while the cool heat transfer fluid C1 is stopped.
  • a second switching cycle of the pump Pf is used to dispense the fluid F1 through its outlet orifice 5.
  • This fluid F1 enters the active element AMR1 and leaves it at a lower temperature F1- to enter the exchanger Ef who uses the frigories. It comes out at a higher temperature F1 and returns to the pump Pf.
  • the active elements AMR1 and AMR2 are each traversed by the same fluid circuit, in which the same heat transfer fluid circulates, alternately in a hot circuit and in a cold circuit.
  • a first gear pump 1 as defined above, referenced Pc is used for the hot circuit
  • a second gear pump 1, referenced Pf for the cold circuit, each circuit comprising a heat exchanger Ec, Ef, whose output is connected to the inlet port 4 of the pump Pc, corresponding Pf.
  • the outlet ports 5 and 6 of each pump Pc, Pf are connected to the input of the active elements AMR1 and AMR2 via a valve 81, 82 with automatic tilting.
  • valve 81, 82 have three inputs and three outputs, between which the fluid is directed by a central shutter, whose position is controlled automatically by the fluid inlet direction inside the valve This valve 81, 82 makes it possible to circulate the same fluid selectively in the hot and cold circuits.
  • the magnetic element CM is opposite the active element AMR1 which heats up in the presence of the magnetic field or an increase in the value of this field.
  • a first switching cycle of the pump Pc is used to dispense the fluid C1 through the outlet orifice 5.
  • the valve 81 directs the fluid C1 into the active element AMR1 which comes out at a higher temperature C1 + to enter the exchanger Ec via the valve 81. It emerges from the exchanger Ec at a lower temperature C1 and returns to the pump Pc.
  • the other active element AMR2 that is not subject to the magnetic field or is subjected to a lower field value, cools down.
  • a first cycle of switching of the pump Pf is used to dispense the fluid F2 through the outlet orifice 6.
  • the valve 82 directs the fluid F2 into the active element AMR2 which leaves it at a lower temperature F2- to enter the fluid. exchanger Ef via the valve 82. It comes out at higher temperature F2 and returns to the pump Pf.
  • the magnetic element CM has moved and is opposite the active element AlVflt2 which heats up in the presence of the magnetic field or an increase in the value of this field.
  • a second switching cycle of the pump Pc is used to dispense the fluid C2 through the outlet orifice 6.
  • the valve 82 directs the fluid C2 into the active element AMR2 which comes out at a higher temperature C2 + to enter the exchanger Ec via the valve 82. It emerges from the exchanger Ec at a lower temperature C2 and returns to the pump Pc.
  • the other active element AMR1 which is not subject to the magnetic field or is subjected to a lower field value, is cooled.
  • a second switching cycle of the pump Pf is used to dispense the fluid F1 through the orifice.
  • the valve 81 directs the fluid F1 in the active element AMR1 which comes out at a lower temperature F1- to enter the exchanger Ef via the valve 81. It comes out at higher temperature F1 and returns to the pump Pf.

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

Claims (15)

  1. Getriebepumpe (1) bestehend aus einem Pumpengehäuse (2) in welchem mindestens zwei ineinander greifende Zahnräder (3) mit parallelen Achsen (A) eingebaut sind, ,die auf einer Seite des Eingriff-Bereichs einen Saugraum (B) und auf der anderen Seite des Eingriff-Bereichs einen Druckraum (C) begrenzen, wobei das besagte Gehäuse mindestens eine Flüssigkeits-Einlassöffnung (4) beträgt, die an mindestens einen Flüssigkeits-Zuführkreis angeschlossen werden kann und die mit dem besagten Saugraum (B) in Verbindung steht, dadurch gekennzeichnet, dass die besagte Pumpe (1) mindestens zwei Flüssigkeits-Auslassöffnungen (5, 6) beträgt, die an mindestens zwei Flüssigkeits-Verbraucherkreise angeschlossen werden können, wobei diese Auslassöffnungen über integrierte Umschaltmittel (7), die angeordnet sind, um die Flüssigkeit abwechselnd nach einem vorbestimmten Umschalt-Zyklus in die besagten Verbraucherkreise aus zu geben, mit dem besagten Druckraum (C) in Verbindung stehen.
  2. Getriebepumpe nach Anspruch 1, dadurch gekennzeichnet, dass der vorbestimmte Umschalt-Zyklus während höchstens einer halben Umdrehung merklich der Drehung der besagten Zahnräder (3) gleich ist.
  3. Getriebepumpe nach Anspruch 1, dadurch gekennzeichnet, dass die besagten Umschaltmittel (7) eine Platte (70) betragen, die flach auf den besagten Zahnrädern (3) aufliegend in dem besagten Gehäuse montiert ist, wobei die Platte (70) mindestens zwei Ausgabekreisläufe (50, 60) beträgt und die Zahnräder (3) jeweils mindestens einen Pufferkanal (30, 40) betragen, wobei die besagten Pufferkanäle (30, 40) angeordnet sind, um während der Drehung der besagten Zahnräder (3) abwechselnd die besagten Ausgabekreisläufe (50, 60) mit der besagten Druckkammer (C) und mit den besagten Auslassöffnungen (5, 6) in Verbindung zu bringen.
  4. Getriebepumpe nach Anspruch 3, dadurch gekennzeichnet, dass die besagten Ausgabekreisläufe (50, 60) und die besagten Pufferkanäle (30, 40) durch in der besagten Platte (70) bzw. in den besagten Zahnräder (3) angeordnete Einsenkungen gebildet sind.
  5. Getriebepumpe nach Anspruch 3, dadurch gekennzeichnet, dass die besagten Pufferkanäle (30, 40) mindestens einen Kreisausschnitt (33, 43) betragen, der jeweils auf der Drehachse (A) jedes Zahnrads (3) zentriert ist, und gegeneinander um den Wert des besagten Kreisausschnitts versetzt sind.
  6. Getriebepumpe nach Anspruch 5, dadurch gekennzeichnet, dass die besagten Kreisausschnitte (33, 43) höchstens gleich 180° sind und gegeneinander um 180° versetzt sind.
  7. Getriebepumpe nach Anspruch 5, dadurch gekennzeichnet, dass jeder Pufferkanal (30, 40) einen der Drehachse (A) des besagten Zahnrads (3) entsprechenden oberstromigen Punkt (31, 41) beträgt, sowie einen unterströmigen Punkt (34, 44), der in dem besagten Kreisausschnitt (33, 43) enthalten ist.
  8. Getriebepumpe nach Anspruch 7, dadurch gekennzeichnet, dass jeder Ausgabekreislauf (50, 60) einen oberstromigen Kanal (51, 61) beträgt, der angeordnet ist, um die Druckkammer (C) mit dem oberstromigen Punkt (31, 41) des ihm entsprechenden Pufferkanals (30, 40) in Verbindung zu setzen, und einen unterstromigen Kanal (54, 64), der angeordnet ist, um den unterstromigen Punkt (34, 44) des Pufferkanals mit der ihm entsprechenden Auslassöffnung (5, 6) in Verbindung zu setzen, wenn der Einlass des besagten unterstromigen Kanals (54, 64) sich gegenüber des besagten Pufferkanals (30, 40) befindet.
  9. Getriebepumpe nach Anspruch 8, dadurch gekennzeichnet, dass der Auslass (53, 63) des oberstromigen Kanals (51, 61) und der Einlass (55, 65) des unterstromigen Kanals (54, 64) in einem Abstand voneinander liegen, der dem Radius des Kreisausschnitts (33, 43) des Pufferkanals (30, 40) merklich gleich ist.
  10. Getriebepumpe nach Anspruch 8, dadurch gekennzeichnet, dass die oberstromigen Kanäle (51, 61) der besagten Ausgabekreisläufe (50, 60) über einen selben, mit der besagten Druckkammer (C) verbundenen Einlass (52, 62) in Verbindung stehen.
  11. Verfahren zur Flüssigkeitsausgabe in mindestens zwei Verbraucherkreisen ausgehend von einem einzigen Zuführkreis, dadurch gekennzeichnet, dass man mindestens eine Getriebepumpe (1) nach irgendwelchem der obigen Ansprüche verwendet, die integrierte Umschaltmittel (7) beträgt, die angeordnet sind, um die besagte Flüssigkeit abwechselnd nach einem vorbestimmten Umschalt-Zyklus in die besagten Verbraucherkreise aus zu geben.
  12. Verfahren zur Flüssigkeitsausgabe in einen warmen Kreislauf und in einen kalten Kreislauf eines Wärmeerzeugers, der einen selben, in einem geschlossenen Kreis zirkulierenden flüssigen Wärmeträger verwendet, dadurch gekennzeichnet, dass man zwei Getriebepumpen (1) nach irgendwelchem der Ansprüche 1 bis 10 verwendet, wobei eine der Pumpen für den warmen Kreislauf und die andere Pumpe für den kalten Kreislauf eingesetzt wird, wobei die besagten Pumpen integrierte Umschaltmittel (7) betragen, die angeordnet sind, um die besagte Flüssigkeit in dem besagten Wärmeerzeuger abwechselnd, je nach Produktion von Kalorien und Frigorien, gemäß eines vorbestimmten Umschalt-Zyklus in Umlauf zu bringen.
  13. Verfahren zur Ausgabe nach Anspruch 12, dadurch gekennzeichnet, dass jede Getriebepumpe (1) mit einem Ventil (81, 82) mit automatischer Umschaltung verbunden ist, das ausgelegt ist, um die besagte Flüssigkeit selektiv in dem besagten warmen Kreislauf und in dem besagten kalten Kreislauf in Umlauf zu bringen.
  14. Verfahren zur Flüssigkeitsausgabe in einem warmen Kreislauf und in einem kalten Kreislauf eines Wärmeerzeugers, der einen ersten flüssigen Wärmeträger für den warmen Kreislauf und einen zweiten flüssigen Wärmeträger für den kalten Kreislauf verwendet, wobei jede Flüssigkeit in einem geschlossenen Kreislauf in Umlauf gebracht wird, dadurch gekennzeichnet, dass man zwei Getriebepumpen (1) nach irgendwelchem der Ansprüche 1 bis 10 verwendet, wobei eine der Pumpen für den warmen Kreislauf und die andere Pumpe für den kalten Kreislauf eingesetzt wird, wobei die besagten Pumpen integrierte Umschaltmittel (7) betragen, die angeordnet sind, um jede Flüssigkeit in dem besagten Wärmeerzeuger abwechselnd, je nach Produktion von Kalorien und Frigorien, gemäß eines vorbestimmten Umschalt-Zyklus in Umlauf zu bringen.
  15. Verfahren zur Ausgabe nach irgendwelchem der Ansprüche 12 bis 14, in dem der besagte Wärmeerzeuger magnetokalorische Elemente (MAR1, AMR2) verwendet, die einer Änderung des Magnetfeldes (CM) unterzogen werden, um die besagten Kalorien und die besagten Frigorien zu erzeugen, dadurch gekennzeichnet, dass man die Drehung der Getriebepumpen (1) mit der besagten Variation des Magnetfelds (CM) synchronisiert.
EP20080828028 2007-07-30 2008-06-23 Getriebepumpe und verfahren zur flüssigkeitsausgabe mittels einer solchen pumpe Not-in-force EP2179181B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0705544A FR2919687B1 (fr) 2007-07-30 2007-07-30 Pompe a engrenage et procede de distribution de fluide utilisant une telle pompe
PCT/FR2008/000879 WO2009024663A2 (fr) 2007-07-30 2008-06-23 Pompe a engrenage et procede de distribution de fluide utilisant une telle pompe

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EP2179181A2 EP2179181A2 (de) 2010-04-28
EP2179181B1 true EP2179181B1 (de) 2011-03-02

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US (1) US8348637B2 (de)
EP (1) EP2179181B1 (de)
JP (1) JP2010535307A (de)
AR (1) AR067622A1 (de)
AT (1) ATE500422T1 (de)
DE (1) DE602008005317D1 (de)
FR (1) FR2919687B1 (de)
TW (1) TW200928104A (de)
WO (1) WO2009024663A2 (de)

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FR2946100B1 (fr) * 2009-05-28 2011-06-03 Centre Nat Etd Spatiales Procede et dispositif d'echeance thermique diphasique a pompe a engrenages sur roulements
JP5316876B2 (ja) * 2009-09-03 2013-10-16 株式会社ジェイテクト ポンプ装置
US9388892B1 (en) 2013-03-11 2016-07-12 Hydro-Gear Limited Partnership Hydrostatic transaxle
FR3003344B1 (fr) 2013-03-14 2018-12-07 Cooltech Applications Appareil thermique
CN105526160A (zh) * 2014-10-16 2016-04-27 德昌电机(深圳)有限公司 齿轮泵
US10851941B2 (en) * 2017-12-04 2020-12-01 Rolls-Royce Corporation Lubrication and scavenge system
DE102019121005A1 (de) * 2019-08-02 2021-02-04 Volkswagen Aktiengesellschaft Pumpe umfassend magnetokalorisches Material

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JP2010535307A (ja) 2010-11-18
WO2009024663A2 (fr) 2009-02-26
DE602008005317D1 (de) 2011-04-14
AR067622A1 (es) 2009-10-14
ATE500422T1 (de) 2011-03-15
TW200928104A (en) 2009-07-01
FR2919687A1 (fr) 2009-02-06
US20100200072A1 (en) 2010-08-12
FR2919687B1 (fr) 2009-09-25
US8348637B2 (en) 2013-01-08
WO2009024663A3 (fr) 2009-07-16
EP2179181A2 (de) 2010-04-28

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