EP0561304B1 - Pompe à engrenages avec contrôle de l'aspiration - Google Patents

Pompe à engrenages avec contrôle de l'aspiration Download PDF

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Publication number
EP0561304B1
EP0561304B1 EP93104085A EP93104085A EP0561304B1 EP 0561304 B1 EP0561304 B1 EP 0561304B1 EP 93104085 A EP93104085 A EP 93104085A EP 93104085 A EP93104085 A EP 93104085A EP 0561304 B1 EP0561304 B1 EP 0561304B1
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EP
European Patent Office
Prior art keywords
pump
throttle
pressure
speed
point
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.)
Expired - Lifetime
Application number
EP93104085A
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German (de)
English (en)
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EP0561304A1 (fr
Inventor
Siegfried A. Dipl.-Ing. Eisenmann
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Individual
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Individual
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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
    • F04C14/24—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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses

Definitions

  • the invention relates to a suction-controlled gerotor pump with the features of the preamble of claim 1.
  • the pump is generally driven by the shaft carrying the pinion.
  • Such pumps are e.g. also used to power hydraulic systems.
  • Such pumps are known from DE-A-39 33 978 of the applicant.
  • the basic wire number values can behave like 10: 1 and above.
  • the delivery target of the lubrication pump of a motor vehicle engine which in automatic transmissions must also take on the function of supplying pressure to the hydraulic switching elements and filling the converter against cavitation, both in the engine and in the transmission only approximately in proportion to the speed in the lower part of the operating range.
  • the oil requirement increases far less than the engine speed.
  • a drive-controlled system is therefore necessary Lubricating or hydraulic pump or such with a speed-dependent adjustable flow rate.
  • the practical characteristics of the delivery rate versus the speed depend on a multitude of parameters, such as delivery pressure, oil viscosity, flow resistance in the suction and pressure line, configuration of the toothing of the gear wheels, width of the gear wheels and design of the pump.
  • Suction control has been developed for the approximate adaptation of the conveyor line to the demand line, for example of an internal combustion engine.
  • the flow resistances in the suction pipe can be determined in such a way that a certain adjustment of the useful delivery rate of a gear pump to the consumption line is achieved. This is e.g. known from DE-A-36 27 414.
  • this pump like the pump according to DE-A-36 27 414, has a large axial extent.
  • the spring valves used can swing and break.
  • the discontinuous connection of the feed cells to the outlet channel is also disadvantageous.
  • the pressure distribution is also related to the Use of cavitation implosions disadvantageous.
  • the overflow channels can preferably be arranged in the teeth of the wheels.
  • the check valves can be designed as ball valves, the ball always striving to press onto the valve seat due to the centrifugal force of the rotary movement of the gearwheel containing the valves.
  • the suction throttle ring pump is controlled in such a way that the throttle cross-section is increased when there is an increased fluid requirement, e.g. by opening a throttle valve in a bypass duct (DE-A-3 627 414) (such a situation arises, for example, in the oil pump of a motor vehicle engine when an exhaust gas turbocharger is switched on If the delivery characteristic curve only changes to the horizontal at a higher speed, the degree of filling of the delivery cells in the suction area is increased when the throttle is opened.
  • the invention wants to avoid this in a pump with the features of the preamble of claim 1.
  • it solves the task of reducing the flow resistance on the pressure side when the throttle is open in the suction channel and thus improving the efficiency and the throughput of the pump, by means of the further development according to the characterizing features of claim 1.
  • the distance of the further outlet opening from the outlet opening which is permanently connected to the outlet channel should be at least equal to the extent of a conveying cell in this direction in the circumferential or circumferential direction of the gearwheels, since otherwise the further outlet opening counteracts an extension of the constantly open outlet opening when the throttle is closed in the outlet channel the direction of funding would work. In this operating state, this would lead to a considerable reduction in the distance and time required for the breakdown of cavitation bubbles.
  • a third outlet opening can be arranged in the conveying direction before the further outlet opening, to which a separate throttle element must then be assigned. This could be opened after reaching an even higher speed or after reaching a higher oil requirement with the resulting parameter values. For the sake of simplicity of construction and control, however, one will usually be satisfied with only one further outlet opening.
  • the throttle element in the derivation from the further outlet opening can be an element that can be opened and closed continuously, such as, for example, such a slide.
  • a throttle element is preferred, which can be switched between a fully closed and fully open position.
  • the control device such that the throttle element in the feed line is opened earlier than the throttle element in the pressure line.
  • three different operating states of the pump can be achieved.
  • In the first state both throttle elements are closed.
  • the pump works normally as it does in the bottom Speed range does.
  • In the second state only the throttle element in the suction channel is open.
  • the pump now pumps more oil; that is, the point at which the conveying characteristic curve changes from the shape which increases proportionally to the speed of rotation into an approximate horizontal is shifted upwards. If the throttle element in the pressure line is also opened when the throughput requirement for the pump increases even further, the delivery rate of the pump is increased further or the above-mentioned change point of the delivery characteristic curve is shifted further up.
  • control device actuates the throttle elements synchronously and in the same direction.
  • control device switches to high flow when a certain pump speed is exceeded and to low flow when it falls below it, it is advantageous if these two switching positions are not at exactly the same speed.
  • the switching speed when the pump speed drops is expediently somewhat lower than the switching speed when the pump speed rises, so that too frequent switching back and forth when the pump is working in the area around the critical speed is avoided.
  • the preferred field of application of the invention is the use of the pump as an oil and / or hydraulic pump for motor vehicle engines and / or gearboxes, in particular automatic gearboxes.
  • the invention is also for other applications, e.g. in hydraulic control systems.
  • the pump shown in FIG. 1 has a pump housing 1 shown in simplified form, in the cylindrical gear chamber of which the ring gear 2 is mounted with its circumference on the peripheral wall of the gear chamber.
  • the shaft 3 carrying the pinion 4 of the gerotor pump is also mounted in the pump housing; however, other positions are also possible.
  • the pinion 4 has one tooth less than the ring gear 2, so that each tooth of the pinion is constantly in engagement with a tooth of the ring gear, as a result of which all the feed cells 13 and 17 formed by the tooth gaps of the pinion and ring gear are constantly sealed against the adjacent cells.
  • the direction of rotation of the pump is clockwise, like indicated by arrow 18.
  • the suction opening 11 is provided in the end wall of the gear chamber lying behind the plane of the drawing in FIG. 1. This is fed via the inlet channel 30, in which a throttle 31 is located.
  • the outlet opening 20 is shown in the top left half. Intake and outlet opening are designed as so-called "kidneys".
  • the outlet line 19 connects to
  • the center points 5 and 6 of the gear wheels 4 and 2 have the center distance or the eccentricity 7, which together with the tip diameter and the width of the gear wheels is responsible for the geometrically specific delivery volume.
  • These geometric variables determine the steepness of the theoretical delivery line 109 of the pump shown in dashed lines in FIG. 5.
  • the intake speed in the inlet channel 30 is low, so that the oil can flow in bubble-free from the intake kidney 11, which extends over almost the entire circumference of the intake side and is arranged in the housing, since no significant negative pressure occurs.
  • the course of the vacuum over the speed is shown in Fig. 6 at 12.
  • the suction cells in positions 13 between the teeth 14 and 15 in engagement are filled with largely bubble-free oil.
  • the inlet channel mouth or suction kidney 11 extends in the circumferential direction up to close to point 16, which is diametrically opposite the point of deepest tooth engagement.
  • point 16 which is diametrically opposite the point of deepest tooth engagement.
  • the delivery cells formed by two tooth gaps opposite each other have reached their greatest volume and are completely filled with oil at low speed.
  • the pump then continues to rotate and the delivery cells reach the area To the left of point 16 in FIG. 1, the cells in positions 17 become displacement cells, since the volume of the delivery cells continuously decreases from here to the point of deepest tooth engagement to almost zero.
  • the outlet opening 20 can also reach close to the point 16.
  • the outlet opening and thus the delivery cell in the first position 17.1 is under full delivery pressure.
  • the outlet opening of the gear chamber or the pressure kidney 20 is shortened very far in the circumferential direction to the point of deepest tooth engagement, as can be seen in FIGS. 1 and 2.
  • the delivery cells must also be able to empty themselves accordingly in positions 17.1 to 71.3 with bubble-free oil filling. This is made possible by the overflow channels 128 in the teeth of the hollow wheel 2.
  • Each overflow channel 128 is provided with a check valve 21.
  • the delivery cells in positions 17.1 to 17.3, in which their volume is steadily decreasing can empty through the series-connected overflow channels 128 with the check valves 21.1 to 21.3 arranged in them in the delivery direction towards the pressure kidney.
  • a somewhat higher static pressure must prevail in the delivery cells in positions 17.1 to 17.3 than in the pressure kidney 20, since the overflow channels 128 with the check valves 21 are lossy with respect to the flow resistance. At low speed these losses are not high because the flow velocities are low. These throttling losses should be kept as small as possible by designing the check valves accordingly.
  • the mouths of the overflow channels and / or the tooth and Tooth gap shapes are of course arranged or dimensioned so that a liquid flow in the direction of pump rotation is prevented at the point of deepest tooth engagement. This is not a problem.
  • a delivery quantity proportional to the speed is delivered. If this limit speed is exceeded, the static pressure in the feed line begins to drop and drops below a critical value, as can best be seen in FIG. 6. In the pump examined, this speed range is around 1200 rpm. From 1450 rpm the flow rate stagnates despite the increasing speed, since the static suction pressure has fallen below the evaporation pressure of the oil. From now on, cavities are created in the delivery cells in positions 13, which theoretically concentrate in the area of the base circle of pinion 4, that is, at 22, since the bubble-free oil is forced radially outwards by centrifugal force. At about 2100 rpm, the pump delivers only 2/3 of its maximum delivery volume, as can be seen from FIG.
  • a dashed level line 23 as a concentric circle to the center of the ring gear.
  • This level line 23 is provided with the level symbol 24. Radially inside the level line there is essentially oil vapor and / or air, radially outside there is essentially oil.
  • the level line 23 passes through the base point 25 of the pinion tooth gap of the delivery cell in position 17.3, which is just about to connect to the pressure kidney or outlet opening 19.
  • the pump is advantageously designed in such a way that even at the maximum operating speeds to be expected, the level line does not move radially further outwards than to the base of the pinion tooth gap of the delivery cell, the is just beginning to reach the edge of the outlet opening 20.
  • This level line can of course always be located radially further inside, as long as the suction control does not suffer.
  • the delivery cells in positions 17.1 to 17.3 are sealed against each other by tooth flanks or tooth head engagement and the check valves in the construction shown are not only due to the centrifugal force acting on the valve ball on the one hand, but also due to the static increase from cell positions 17.1 to 17.2 to 17.3 Pressure are closed, the delivery pressure in the outlet opening 20 cannot act into the delivery cells in positions 17.1 to 17.3.
  • the cavities 26 within the leveling ring surface 23 thus have enough time to reduce until the position 17.3 is reached by reducing the cell volume.
  • the pump is known from DE 39 33 978 C2.
  • the invention now seeks to ensure that the point at which the flow rate characteristic curve 109 bends horizontally in FIG. 5, when a corresponding parameter of the device fed by the pump, in particular thus an internal combustion engine or an automatic motor vehicle transmission, has reached a further point position 102 is shifted.
  • a bypass channel 33 is assigned to the inlet channel which leads through the diaphragm 31, in which a throttle valve 43 is located, which between a fully extended blocking position in FIG. 1 and one the flow can be adjusted by the channel 33 releasing, dashed position.
  • the pressure or drain channel 19 is not only fed from the pressure kidney 20, but also from an outlet opening 35 connected upstream of this pressure kidney 20, which is connected via the channel 36 to the outlet channel 19 in the manner shown in FIG. 1.
  • a throttle valve 37 which can be switched between a position blocking the channel 36, shown in solid lines in FIG. 1, and a position in FIG. 1 which shows the flow through this channel 36.
  • the pump is the lubricating oil pump of a motor vehicle drive engine, which can be brought to higher performance by switching on an exhaust gas turbocharger.
  • the two throttle valves 43 and 37 are closed.
  • the pump now works in the usual way as a suction-controlled pump. Its characteristic curve 109 bends horizontally in the area of point 101. If, because the exhaust gas turbocharger is switched on, larger amounts of oil are required, the control device 38, which is only indicated schematically in FIG. 2, switches the two throttle valves 43 and 37 from the closed position into the open position. As a result, the suction resistance is greatly reduced and the level line 23 is correspondingly shifted inwards. That is, in FIG. 5, the bend in the delivery characteristic moves from position 101 to position 102.
  • the drive power Pantr and the absorbed torque Md are also entered in FIG. 5. All values are shown both for a pump pressure of 2 bar and for a pressure of 4 bar.
  • the throttle arrangement in the inlet duct 30 is shown somewhat differently than in FIG. 1 in order to indicate that the invention is not restricted to the arrangement of a throttle valve parallel to a rigid throttle.
  • a throttle valve 43 can be used, which can not be switched between a fully closing and fully opening position, but between a partially closing and fully opening position. In this way, the separate bypass channel 33 and the rigid diaphragm 31 can be omitted, since the throttle valve takes over both functions at the same time.
  • the two throttle valves 33 and 37 can function functionally as shut-off valves as previously described. However, with appropriate control, they can also be continuously adjustable in order to meet a constantly changing fluid requirement. 5 does not jump from 101 to 102 and back, but can assume any desired position between these two points.
  • a further pressure kidney 39 in addition to the upstream pressure kidney 35; this is the one Druckniere 35 again upstream by a corresponding piece.
  • the pressure kidney 39 then feeds the pressure line 19 via a line 203 and a shut-off valve 204 located therein.
  • the throttles 37 and 43 from the example according to FIG. 1 are replaced by shut-off valves 205 and 207.

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

Claims (4)

  1. Pompe à engrenages avec contrôle de l'aspiration, en particulier pompe à huile et/ou pompe hydraulique pour des moteurs et/ou boîtes de vitesses de véhicules automobiles, comprenant
    - un carter,
    - une roue à denture intérieure (2) montée de manière tournante dans une chambre à engrenages du carter (1),
    - un pignon (4) présentant une dent de moins que la roue à denture intérieure (2) et en prise avec ladite roue à denture intérieure (2), dont les dents forment, conjointement avec les dents de la roue à denture intérieure (2), des cellules de refoulement (17) dont le volume augmente (13) pour diminuer ensuite (17), qui se succèdent et sont rendues étanches les unes par rapport aux autres, et qui communiquent respectivement avec les cellules de refoulement voisines par des canaux de trop-plein prévus dans la roue à denture intérieure et/ou dans le pignon,
    - des clapets antiretour dans les canaux de trop-plein qui s'opposent à un écoulement du fluide d'actionnement dans le sens opposé à la direction de refoulement
    - des canaux d'admission et d'évacuation disposés dans le carter (1) pour l'amenée et l'évacuation du fluide d'actionnement,qui débouchent dans la chambre à engrenages,de part et d'autre du point d'engrènement le plus bas (10,19),l'extrémité de l'embouchure du canal de sortie opposée au point d'engrènement le plus bas étant située suffisamment près du point d'engrènement le plus bas pour que plusieurs cellules de refoulement diminuant de volume se trouvent toujours entre ladite extrémité et le point périphérique auquel commence la diminution du volume desdites cellules de refoulement, et
    - un système d'étranglement variable prévu dans le canal d'admission,
    caractérisée en ce que
    - l'embouchure (20) du canal d'évacuation (19) est précédée à distance, dans la direction circonférentielle de la pompe, d'au moins une autre embouchure (35) communiquant avec le canal d'évacuation (19), qui est raccordée par une conduite (36) avec le canal d'évacuation (19),
    - le passage par cette conduite (36) peut être commandé, et notamment bloqué, au moyen d'un élément d'étranglement (37) , et que
    - un dispositif de commande (38) est prévu pour le système d'étranglement (43, 207) muni d'éléments d'étranglement et pour l'élément d'étranglement (37).
  2. Pompe à engrenages selon la revendication 1, caractérisée en ce que le dispositif de commande (38) actionne les éléments d'étranglement (37, 43, 204, 205) de manière synchrone et dans le même sens.
  3. Pompe à engrenages selon l'une des revendications 1 ou 2, caractérisée en ce que le dispositif de commande (38) commute les éléments d'étranglement (37, 43, 204, 205) entre respectivement deux positions.
  4. Pompe à engrenages selon l'une des revendications 1, 2 ou 3, caractérisée en ce que le dispositif de commande (38) commute sur grand débit dès le dépassement d'une vitesse de rotation déterminée de la pompe, et sur débit faible lorsqu'une vitesse de rotation légèrement inférieure est dépassée vers le bas.
EP93104085A 1992-03-20 1993-03-12 Pompe à engrenages avec contrôle de l'aspiration Expired - Lifetime EP0561304B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4209143A DE4209143C1 (fr) 1992-03-20 1992-03-20
DE4209143 1992-03-20

Publications (2)

Publication Number Publication Date
EP0561304A1 EP0561304A1 (fr) 1993-09-22
EP0561304B1 true EP0561304B1 (fr) 1994-10-26

Family

ID=6454643

Family Applications (1)

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EP93104085A Expired - Lifetime EP0561304B1 (fr) 1992-03-20 1993-03-12 Pompe à engrenages avec contrôle de l'aspiration

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US (1) US5380169A (fr)
EP (1) EP0561304B1 (fr)
JP (1) JP2740107B2 (fr)
DE (1) DE4209143C1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9324501D0 (en) * 1993-11-30 1994-01-19 Hobourn Automotive Ltd Positive displacement pumps
DE4437076C2 (de) * 1994-10-17 1998-02-05 Eisenmann Siegfried A Ventilsteuerung mit sauggeregelter Zahnringpumpe
CA2159672C (fr) * 1994-10-17 2009-09-15 Siegfried A. Eisenmann Soupape et dispositif de commande a couronne commandee pr aspiration et pompe a engrenages interieurs
DE10127916A1 (de) * 2001-06-08 2002-12-12 Daimler Chrysler Ag Abgasturbolader
EP1522722B1 (fr) * 2003-10-06 2006-12-20 Ford Global Technologies, LLC, A subsidary of Ford Motor Company Moteur à combustion et méthod pour controller l'arrêt d'un moteur à combustion
JP5576191B2 (ja) * 2010-06-18 2014-08-20 トヨタ自動車株式会社 車両用内接歯車型オイルポンプ
JP6144039B2 (ja) * 2012-11-28 2017-06-07 豊興工業株式会社 内接歯車ポンプ
JP6470613B2 (ja) * 2015-03-30 2019-02-13 株式会社Ｓｕｂａｒｕ オイルポンプ
JP6470612B2 (ja) * 2015-03-30 2019-02-13 株式会社Ｓｕｂａｒｕ オイルポンプ
US10989191B2 (en) * 2018-03-28 2021-04-27 Schaeffler Technologies AG & Co. KG Integrated motor and pump including radially movable outer gerator
DE102022203867A1 (de) * 2022-04-20 2023-10-26 Hanon Systems Efp Deutschland Gmbh Gerotorpumpe

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3067689A (en) * 1958-10-06 1962-12-11 Gen Motors Corp Variable capacity fluid supply
DE3005657C2 (de) * 1980-02-15 1987-01-02 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Zahnradpumpe
DE3506629A1 (de) * 1984-03-01 1985-10-03 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Hydrauliksysteme
WO1985004455A1 (fr) * 1984-03-29 1985-10-10 Zahnradfabrik Friedrichshafen Ag Systeme hydraulique pour vehicules
DE3627414A1 (de) * 1986-08-13 1988-02-18 Barmag Barmer Maschf Verbrennungsmotor
DE3824398C2 (de) * 1987-07-23 1993-11-18 Barmag Barmer Maschf Schmierölpumpe
DE3933978A1 (de) * 1989-10-11 1991-05-02 Eisenmann Siegfried A Sauggeregelte zahnringpumpe

Also Published As

Publication number Publication date
EP0561304A1 (fr) 1993-09-22
DE4209143C1 (fr) 1993-04-15
JP2740107B2 (ja) 1998-04-15
US5380169A (en) 1995-01-10
JPH0617765A (ja) 1994-01-25

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