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EP0619430B1 - Pompe à engrenage internes pour gamme de vitesses rotatives élévées - Google Patents

Pompe à engrenage internes pour gamme de vitesses rotatives élévées Download PDF

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Publication number
EP0619430B1
EP0619430B1 EP93121068A EP93121068A EP0619430B1 EP 0619430 B1 EP0619430 B1 EP 0619430B1 EP 93121068 A EP93121068 A EP 93121068A EP 93121068 A EP93121068 A EP 93121068A EP 0619430 B1 EP0619430 B1 EP 0619430B1
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EP
European Patent Office
Prior art keywords
opening
tooth
gear pump
orifice
internal gear
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
EP93121068A
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German (de)
English (en)
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EP0619430A1 (fr
Inventor
Siegfried A. Dipl.-Ing. Eisenmann
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Individual
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Individual
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Priority claimed from DE4330586A external-priority patent/DE4330586A1/de
Application filed by Individual filed Critical Individual
Publication of EP0619430A1 publication Critical patent/EP0619430A1/fr
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Publication of EP0619430B1 publication Critical patent/EP0619430B1/fr
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Expired - Lifetime legal-status Critical Current

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    • 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 an internal gear pump, which can be designed both as a gerotor pump and as a filling pump according to the preamble of patent claim 1.
  • Such internal gear pumps have to travel through a very large speed range. They should have good volumetric efficiency at low speed, so they must be designed with narrow leakage gaps. At the same time, however, they should at the same time not cause any cavitation noises as a result of steam and air bubble cavitation when the medium is transferred from the suction side to the pressure side of the pump.
  • These gear pumps are preferred as Lubrication, feed and switching pumps are used in internal combustion engines and automatic transmissions, in which cavitation noises in particular are perceived as very annoying.
  • FIG. 1 shows the delivery flow QH (ordinate) as a function of the speed n (abscissa) and the deviation of the delivery line from the linear range from a critical speed n crit .
  • the funding line will then become increasingly flatter.
  • the degree of filling is therefore less than 1, so that there is a medium deficit in the tooth chambers in relation to the geometric delivery volume.
  • the deficit area is partly filled with steam from the pumped medium, partly with air that has been separated from the medium and partly with "incorrect air” drawn in through leaks.
  • This critical speed is basically determined by a critical peripheral speed in the toothing area, at which, according to Bernoulli's law, the static pressure in the liquid is more and more consumed by the speed pressure (dynamic pressure). If the static pressure falls below the vapor pressure of the liquid, bubbles form which are below the reduced static pressure and only condense again when the static pressure of the bubble rises above the vapor pressure.
  • the critical speed of the gear pumps considered here almost does not depend on the viscosity of the medium. Normally one would expect that the critical speed would be much lower with very viscous medium than with thin medium. However, this is not the case. A plausible explanation for this phenomenon is seen in the fact that the speed pressure is linear only from the specific mass and from the square of the speed depends. For similar pumps with roughly the same peripheral speed, the critical speed is therefore almost exactly at the same point, regardless of the viscosity and the design of the pump (e.g. whether with or without a filler). It has hardly ever been possible to significantly influence the value of the critical speed above which the pumps become significantly louder by modifying the tooth flank shapes or the inlet channel in the housing or by other design measures.
  • the pinion has only one tooth less than the toothed ring
  • the pump is therefore a so-called gerotor pump, in which each tooth of the pinion constantly interacts with the toothing of the toothed ring.
  • any form of toothing can be used that is suitable for a gerotor pump and ensures a sufficient seal between the teeth of the pinion and toothed ring even in the pressure range of the pump.
  • a pure cycloid toothing in which the tooth heads and gaps of the wheels have the profile of cycloids, which are formed by rolling rolling circles on fixed circles concentric to the respective wheel axes, the tooth heads of the pinion and the tooth gaps of the Toothed rings each have the shape of epicycloids, which are formed by rolling a first rolling circle, the tooth gaps of the pinion and the tooth tips of the toothed ring each have the shape of hypocycloids, which are formed by rolling a second rolling circle, and the sum of the circumferences of the two rolling circles is the same as the tooth pitch of the wheels on their fixed circles.
  • Examples of such gearing are described in German specification 39 38 346.6 and German patent application P 42 00 883.2-15.
  • the difference in the number of teeth of the pinion and the toothed ring can also be greater than one. However, it should not be large so that you can use a relatively small medium number of teeth and thus maintains large cells. It is therefore preferred that the difference in the number of teeth is not greater than three.
  • a filler must be provided in the area opposite the point of deepest tooth engagement in the usual way, which fills at least the middle part of the free space in the circumferential direction between the tip circles of the two gear wheels and thus ensures the required seal there.
  • This type of pump is particularly quiet.
  • Such pumps are suitable for. B. for feeding hydraulic systems.
  • such pumps are used as oil or hydraulic pumps for motor vehicle engines and / or gearboxes.
  • Motor vehicle engines and gearboxes are operated in a wide range of speeds.
  • the basic speed values can behave like 12: 1 and above.
  • the delivery target of the lubrication pump of a motor vehicle engine which in automatic transmissions also has to take on the function of supplying pressure to the hydraulic switching elements and filling the converter to protect against cavitation, is only approximately proportional to the speed in both the engine and the transmission in the lower third of the operating range. In the upper speed range, the oil requirement increases far less than the engine speed. It is therefore desirable to have a drive-controlled lubrication or hydraulic pump or one with a speed-adjustable output.
  • the suction control is to avoid loss of a certain pump speed. Since the flow resistances increase disproportionately with increasing oil speed, the static pressure in the suction opening of the gear chamber drops more and more with a throttle in the suction line until the so-called cavitation pressure threshold is reached, i.e. until the vapor pressure of the oil is undercut.
  • the content of the feed cell then consists partly of liquid oil, partly of oil vapor, partly also of sucked-in air, whereby it is under a static pressure that is significantly below atmospheric pressure.
  • the cell contents are given sufficient time to increase the static pressure to a sufficient extent by gradual compression so that when a cell connects to the outlet channel, in no more implosions of gas bubbles can take place because the latter have already condensed to liquid again or have dissolved in the liquid due to the constant reduction in the cell volume.
  • the shrinking delivery cells must be sealed so well against each other that the discharge pressure is separated from one another by the gap between the two, two successive delivery cells separating teeth can not reproduce significantly against the direction of conveyance.
  • This pump has a correspondingly large axial extension.
  • the spring valves used can break.
  • the discontinuous connection of the feed cells to the outlet channel is also disadvantageous.
  • the pressure distribution is unfavorable to avoid cavitation implosions and the pump operates loudly.
  • gerotor pump known from German patent specification 39 33 978 is considerably more advantageous, in which the problem of squeezing oil discharge in the downsizing delivery cells at low speed and cavitation-free operation is solved in that in the teeth of at least one gearwheel the channels connecting the respective tooth connecting channels are provided in which are check valves that only allow flow through the respective channel in the conveying direction.
  • this pump also still works undesirably loud at higher speeds.
  • An internal gear pump according to the preamble of claim 1 is known from JP 05-44651.
  • a narrow channel coming from the outlet opening and running in the circumferential direction extends in the end face of the pump housing through the region of the delivery cells on the pressure side.
  • this channel is not designed in such a way that its flow resistance in the high speed range could counteract the development of cavitation to a particular degree.
  • the object of the present invention is to noticeably reduce the noise caused by cavitation in an internal gear pump of the type specified.
  • the advantages achieved with the invention are based on the following mode of operation:
  • the time span of the static pressure increase in the delivery cells will be extended in the circumferential direction to a sufficient extent so that the pressure gradient dp / dt becomes smaller. This gives the bubbles enough time to dissolve or condense even in the low pressure range. This avoids the feared violent implosion of the bubbles under high pressure, which leads to noise and cavitation damage.
  • this extension of the compression phase must not lead to squeezing when the cells are filled 100% with compact liquid, ie in the lower speed range. This would then lead to different types of noise and loss of performance.
  • pinch oil can flow out of the shrinking delivery cells into an outlet channel through an opening. If the pump is running at low speed, all feed cells in the suction area of the pump are filled with working fluid. These full conveyor cells cut the opening or openings in the pressure area before they can significantly reduce in size. During the then reducing the size of the delivery cells, the pinch oil flows through a connecting channel into the outlet channel. If the speed continues to increase until cavitation occurs in the inlet mouth and the area of the enlarging conveyor cells, the current in the connecting channel to the outlet channel slows down, in order to come to a standstill when the speed continues to increase and finally even to reverse.
  • the impedance generated by the constant acceleration and deceleration of the liquid column in the connection channel does not yet play a role, since the processes here take place correspondingly slower.
  • the pinch oil can flow out through the opening (s) and the connecting channel. The transition from one state to another in the connection channel is continuous.
  • Each opening is completely or at least largely covered by a tooth each time it overflows.
  • the connecting duct preferably leads via the outlet mouth into the outlet duct.
  • the opening is kept small in comparison with the mouth of the outlet duct and the cross section of the connecting duct is small in comparison with that of the outlet duct.
  • the ratio of the size of the opening to that of the mouth of the outlet channel and the cross section of the connecting channel to that of the outlet channel can be, for example, 5% or 10%.
  • a certain length of the connecting channel is of course also indicated. However, this arises automatically since the opening must naturally have a certain distance from the outlet channel opening. In general it can be said that the length of the connecting channel should be a multiple of the characteristic length of its cross section.
  • the height of the impedance can also be influenced by the arrangement of the opening in the radial direction. The closer the opening is to the root circle of the gearwheel, the longer the period in which the opening is covered by teeth, in comparison with the period in which the opening lies opposite tooth gaps, that is to say open to delivery cells.
  • the opening is formed as a groove extending in the circumferential direction near the root circle of the toothing of the pinion, or better, the ring gear, in an end wall of the gear chamber.
  • the training in the area of the base circle of the ring gear is preferred because there is more space here for the arrangement of the opening and the connecting channel.
  • the extent of the opening in the radial direction is preferably one fifth to one third of the height of the teeth sweeping over it.
  • the connecting duct can, for example, open directly into the outlet duct and be cast into the wall of the pump housing as a tubular duct.
  • the connecting channel is formed as a groove in the wall of the gear chamber, which is covered by the body of the gear carrying the sweeping teeth. This groove is advantageously located in the end wall of the gear chamber and not in the peripheral wall. The latter becomes more complex when the groove is machined mechanically.
  • the number of openings is preferably at most one less than the maximum number of closed feed cells between the start point of the feed cell reduction and the start of the pressure opening.
  • these can advantageously be arranged one behind the other in the circumferential direction and have a distance in this direction of approximately 1/2 tooth pitch from one another. This does not mean the distance between the opening centers, but rather the distance between the opening edges facing each other from each other.
  • each opening - its number will not be large in practice for pumps for motor vehicle engines and gearboxes - can be connected to the outlet channel via a separate connecting channel.
  • the openings are preferably connected to the outlet channel via a common connecting channel.
  • the distance of the opening from the mouth of the outlet channel in the circumferential direction is approximately equal to half the distance between the end of the mouth of the inlet channel and the end of the mouth of the outlet channel.
  • the distance of the opening from the filler measured in the conveying direction is preferably approximately zero.
  • a preferred embodiment of the internal gear pump according to the invention has a suction control with a fixed or variable throttle provided in the inlet duct.
  • the extent of the openings in the circumferential direction is preferably approximately equal to the thickness of the teeth sweeping over them at the radial height of the opening. This ensures a sufficient squeezing oil flow at low speed and a sufficiently high throttling at high speed.
  • the arrangement of the opening in the circumferential direction is also essential.
  • the distance of the opening from the mouth of the outlet channel is preferably in Circumferential direction approximately equal to the tooth pitch.
  • the reference numeral 20 On the left side of the housing shown in FIG. 2 is the reference numeral 20, which is also a trough designated outlet mouth or kidney 20 formed in the housing wall. Below the mouth 20, the connecting channel 33 formed there and at its end opposite the flow direction, the opening 30 is indicated.
  • the pump shown schematically in Fig. 3 has a pump housing 1, from which the cover is removed, so that the cylindrical gear chamber 2 is open and can be seen, in which a toothed ring 3 is mounted with its periphery on a peripheral wall 8 of the gear chamber 2. Also in the gear chamber 2 is a pinion 4, which is carried by a drive shaft 13 of the pump. In this respect, other positions are also possible.
  • the pinion has ten teeth and the toothed ring 2 has eleven teeth.
  • the toothing is one in which all teeth of the pinion 4 are constantly in engagement with the toothing of the toothed ring 3.
  • all of the conveyor cells 13 and 17 formed by the tooth gaps of the pinion and ring gear are constantly adequately sealed against the adjacent conveyor cells.
  • the direction of rotation of the pump is clockwise, as indicated by the arrow on the shaft 13.
  • the toothing of the gears is a pure cycloid toothing.
  • the tooth heads and tooth gaps of both the toothed ring and the pinion have the profile of cycloids, which are formed on the pitch circle of the respective wheel by the rolling off of small roller circles, the circumference of which is equal to half a tooth pitch.
  • the tooth tips of the pinion and the tooth spaces of the toothed ring each have the shape of epicycloids, while the tooth spaces of the pinion and the tooth tips of the toothed ring each have the shape of hypocycloids.
  • the diameters of the roll circles forming the epicycloids are equal to the diameter of the roll circles forming the hypocycloids.
  • a suction opening 11 is provided, which is partially covered in FIG. 3 by the gear wheels 3 and 4 shown broken off.
  • the tooth contour of the two gear wheels in Fig. 1 is shown in dash-dotted lines over the remaining circumference.
  • the center of the toothed ring 3 is indicated at 5, the center of the pinion 4 at 6.
  • the point of deepest meshing is shown at 7; the point 23 of the tooth vertex contact is diametrically opposite the point 7.
  • the mouth 11 of the inlet channel 12 which is worked out as a depression in this end wall and into which a diaphragm 14 serving for suction control is inserted.
  • the mouth 11 is also referred to as a suction kidney. It extends in the circumferential direction from a point near the point 7 of deepest tooth engagement to close to the point 23 of the vertex contact.
  • the mouth 20 of the outlet channel 21 is also formed as a recess in the visible end wall 22 of the gear chamber 2.
  • the outlet mouth or kidney 20 is substantially smaller than the inlet mouth 11. While this is in the direction of rotation lying end of the outlet mouth 20 has approximately the same distance from the point 7 of deepest tooth engagement as the inlet mouth 11, the end of the outlet mouth 20 opposite the direction of rotation from the point 7 of deepest tooth engagement has only a distance of approximately 80 °.
  • the design of the pump housing is known.
  • Fig. 3 one recognizes on the way from the point 23 of the tooth vertex contact to the beginning of the outlet mouth 20 three conveyor cells 17, 17.1 and 17.2 surrounded by the dash-dotted lines, which migrate fluid from the clockwise Promote inlet mouth 11 to outlet mouth 20.
  • Two openings 30 and 31 are provided in the end wall 22 of the gear wheel chamber 2 corresponding to the relatively large number of teeth here, which extend in this end wall in the circumferential direction.
  • the openings 30 and 31 run close to the root circle of the toothing of the toothed ring 3 within this root circle.
  • Each of the two openings 30 and 31 is connected via a short, radially outwardly extending channel piece to the circumferentially extending connecting channel 33, which is connected to the mouth 20 of the outlet channel.
  • the radial channel parts, the openings 30, 31 and the connecting channel 33 are formed as grooves in the end wall 22 of the gear chamber 2.
  • the connecting channel 33 is constantly covered by the ring part of the toothed ring 3 which supports the teeth.
  • the end of the first opening 30 facing this point in the circumferential direction can have a relatively large angular distance from this point, which here is about two thirds of the tooth pitch measured in angular dimension this opening 30 is over the ring gear.
  • the end of the opening 31 located in the conveying direction is considerably further away from the facing end of the outlet mouth 20, namely slightly more than one tooth pitch, so that whenever a conveying cell loses contact with the opening 31, it immediately begins to get into the Open outlet mouth 20.
  • the distance between the facing ends of the two openings 30 and 31 is so great that the two openings 30 and 31 are never connected by a conveyor cell; it can also be slightly larger if the openings are narrow.
  • the radial position of these openings must also be taken into account.
  • the extent of the openings 30, 31 in the circumferential direction must be smaller the more the opening lies away from the tooth root circle of the toothed ring 3.
  • the opening 30 is located somewhat further radially inward than the opening 31, but is also shown somewhat shorter than the latter. Both openings are relatively short in the example shown, in many cases they will also be able to be formed somewhat longer.
  • the squeezed oil flow QL through the channel 33 corresponds to the displacement volume of the delivery cells 17, 17.1 and 17.2.
  • the apparent flow resistance for the flow through the channel 33 now increases, since the open times for the openings 30 and 31 are becoming shorter and shorter.
  • the pressure PI in the cells 17, 17.1 and 17.2 increases with a simultaneous drop in the pinch oil flow QL through the line 33.
  • these conditions only apply up to the speed at which there is still no cavitation in the suction mouth 11, that is to say in the delivery cells 13, occurs. In the cavitation area at a higher speed, where the conveyor line (FIG.
  • Fig. 7 shows the corresponding suction pressure PS in the inlet mouth as a function the speed
  • Figure 8 represents the intermediate pressure PI and the pressure difference Pi-PH as a function of the speed n for such a pump.
  • the openings 30, 31 and the channel are formed by a single serpentine groove, which (clockwise) in Fig. 3 from the right end of the opening 30 to the left end of the same, then horizontally to the left in the channel 33 and this follows until it runs approximately vertically upwards to the lower end of the opening 31, follows this to the upper end and finally leads from this again to the left into the channel 33, which it then follows to the opening 20.
  • the openings 30, 31 are designed to run in the spiral direction or also circular.
  • the pump shown in FIG. 4 has a housing 41, in which a toothed ring 43 is mounted, which meshes with a pinion 44.
  • An inlet 52 in which an orifice 54 is provided for suction control, feeds an inlet mouth 51, while an outlet mouth 60 is connected to an outlet channel 61.
  • the pinion 44 here has two teeth less than the toothed ring 43, so that a filler piece must be arranged opposite the point of deepest tooth engagement, ie in FIG. 4 below, in order to effect the required seal there .
  • the direction of rotation of the pump is clockwise.
  • the filler 60 is shortened at both ends, as can be seen from the drawing, since an excessively thin leakage of the filler, which is in itself narrow, would lead to undesirable fluttering.
  • the ends of the filler are cut off so that one tooth of the pinion and one tooth of the toothed ring come into and out of engagement with the filler simultaneously.
  • each tooth of the pinion is in constant engagement with the toothing of the toothed ring.
  • two openings 70 and 71 are now also provided here in the area between the end of the filler 60 lying in the conveying direction and the end of the outlet mouth 60 opposite the conveying direction.
  • the two openings 70 and 71 are connected to the mouth 60 of the outlet channel 61 via the connecting channel 73.

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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 (12)

  1. Pompe à engrenages internes pour régimes élevés, comprenant un carter (1, 41) contenant une chambre à engrenages (2), un anneau denté (3, 43) dans le carter (1, 41), un pignon (4, 44) qui comporte une dent ou seulement quelques dents de moins que l'anneau denté (3, 43), s'engrène avec l'anneau denté (3, 43), est disposé dans celui-ci, et dont les dents forment, conjointement avec celles de l'anneau denté (3, 43), et étanchent les uns par rapport aux autres des alvéoles successifs (13, 17, 17.1, 17.2) qui croissent et décroissent à nouveau et qui servent à refouler le liquide de travail, des canaux d'entrée et de sortie (12, 21, 52, 61) qui traversent le carter (1, 41) et servent à admettre et à évacuer le liquide de travail et qui débouchent dans la chambre à engrenages (2) de part et d'autre du point (7) d'engrènement maximal, les alvéoles de refoulement (17, 17.1, 17.2, 13) défilant devant ces embouchures (11, 20, 51, 62), et de plus l'extrémité de l'embouchure (20, 62) du canal de sortie (21, 61) située à l'opposé du point (7) d'engrènement maximal étant suffisamment proche du point (7) d'engrènement maximal pour que, entre elle et le point où les alvéoles de refoulement (17) commencent à décroître, se trouve toujours plus d'un alvéole de refoulement (17, 17.1, 17.2), caractérisée en ce que, dans la zone des alvéoles de refoulement décroissants est ménagée, dans la paroi de la chambre à engrenages (2), dans le sens circonférentiel à distance de l'embouchure (20, 62) du canal de sortie (21, 61), au moins une ouverture (30, 31, 70, 71) devant laquelle défilent alternativement des alvéoles de refoulement (17, 17.1, 17.2) et les dents qui les délimitent, en ce que l'ouverture (30, 31, 70, 71) communique avec le canal de sortie par un canal de liaison (33, 73), en ce que, au passage de chaque dent, l'ouverture (30, 31, 70, 71) est recouverte entièrement ou au moins en grande partie par celle-ci, et en ce que l'ouverture (30, 31, 70, 71) se présente sous la forme d'une gorge qui est pratiquée dans l'une des parois frontales (22) de la chambre à engrenages (2) et qui s'étend dans le sens circonférentiel à proximité du cercle de pied de la denture du pignon (4) ou, comme c'est préférable, de la roue à denture intérieure (3).
  2. Pompe à engrenages internes selon la revendication 1, caractérisée en ce que l'ouverture (30, 31, 70, 71) est petite par rapport à l'embouchure (20, 62) du canal de sortie (21, 61), et la section du canal de liaison (33, 73) est petite par rapport à celle du canal de sortie (21, 61).
  3. Pompe à engrenages internes selon la revendication 1 ou 2, caractérisée en ce que l'extension des ouvertures (30, 31, 70, 71) dans le sens radial est comprise entre un cinquième et un tiers de la hauteur des dents qui défilent devant elles.
  4. Pompe à engrenages internes selon l'une des revendications 1 à 3, caractérisée en ce que le canal de liaison (33, 73) se présente sous la forme d'une gorge qui est pratiquée dans la paroi (22) de la chambre à engrenages (2) et qui est recouverte par le corps de la roue dentée (3, 43) portant les dents défilantes.
  5. Pompe à engrenages internes selon la revendication 4, caractérisée en ce que le canal de liaison (33, 73) dérive radialement de l'ouverture (30, 31, 70, 71).
  6. Pompe à engrenages internes possédant une différence numérique de dents égale à un selon l'une des revendications 1 à 5, caractérisée en ce que la distance entre l'ouverture (30, 31, 73) et l'embouchure (20, 62) du canal de sortie (21, 61) dans le sens circonférentiel est sensiblement égale à la moitié de la distance entre l'extrémité de l'embouchure du canal d'entrée et l'extrémité de l'embouchure du canal de sortie.
  7. Pompe à engrenages internes possédant une différence numérique de dents supérieure à un et une pièce intercalaire (60) dans l'espace situé entre les cercles de tête des roues dentées (43, 44) à l'opposé du point d'engrènement maximal selon l'une des revendications 1 à 5, caractérisée en ce que, mesurée dans la direction de refoulement, la distance entre l'ouverture (70) et l'extrémité côté refoulement de la pièce intercalaire (60) est sensiblement égale à zéro.
  8. Pompe à engrenages internes selon l'une des revendications 1 à 7, caractérisée en ce que, en présence de plusieurs ouvertures (30, 31, 70, 71) disposées l'une derrière l'autre dans le sens circonférentiel, celles-ci sont distantes d'environ la moitié d'un pas de dent.
  9. Pompe à engrenages internes selon la revendication 8, caractérisée en ce que les ouvertures (30, 31, 70, 71) communiquent avec l'embouchure de sortie (20, 62) par un canal de liaison commun (33, 73).
  10. Pompe à engrenages internes selon l'une des revendications 1 à 9, caractérisée en ce qu'elle comporte un moyen de régulation de l'aspiration comprenant un étranglement (14, 54) monté de manière fixe ou mobile dans le canal d'entrée (12, 52).
  11. Pompe à engrenages internes selon l'une des revendications 1 à 10, caractérisée en ce que l'extension de l'ouverture (30, 31, 70, 31) dans le sens circonférentiel est approximativement égale à l'épaisseur des dents qui défilent devant elles sur la hauteur de l'ouverture.
  12. Pompe à engrenages internes selon l'une des revendications 1 à 11, caractérisée en ce que la distance entre l'ouverture (31, 73) et l'embouchure (20, 62) du canal de sortie dans le sens circonférentiel est sensiblement égale au pas des dents.
EP93121068A 1993-03-05 1993-12-29 Pompe à engrenage internes pour gamme de vitesses rotatives élévées Expired - Lifetime EP0619430B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE4307034 1993-03-05
DE4307034 1993-03-05
DE4330586 1993-09-09
DE4330586A DE4330586A1 (de) 1993-03-05 1993-09-09 Innenzahnradpumpe für großen Drehzahlbereich

Publications (2)

Publication Number Publication Date
EP0619430A1 EP0619430A1 (fr) 1994-10-12
EP0619430B1 true EP0619430B1 (fr) 1997-07-23

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EP93121068A Expired - Lifetime EP0619430B1 (fr) 1993-03-05 1993-12-29 Pompe à engrenage internes pour gamme de vitesses rotatives élévées

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US (1) US5413470A (fr)
EP (1) EP0619430B1 (fr)
JP (1) JP2739034B2 (fr)
CN (1) CN1040352C (fr)
CA (1) CA2115795C (fr)

Families Citing this family (21)

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Publication number Priority date Publication date Assignee Title
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
JP2654373B2 (ja) * 1995-03-14 1997-09-17 東京焼結金属株式会社 内接歯車式流体装置
DE19543962A1 (de) * 1995-11-25 1997-05-28 Bosch Gmbh Robert Hydraulische Fahrzeugbremsanlage mit Radschlupfregeleinrichtung
DE19546292A1 (de) * 1995-12-12 1997-06-19 Zahnradfabrik Friedrichshafen Verfahren zur automatisierten Abstimmung des Befüllvorganges von Schaltelementen
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CN1103136A (zh) 1995-05-31
JP2739034B2 (ja) 1998-04-08
US5413470A (en) 1995-05-09
CA2115795C (fr) 2000-04-11
EP0619430A1 (fr) 1994-10-12
CA2115795A1 (fr) 1994-09-06
JPH06299972A (ja) 1994-10-25
CN1040352C (zh) 1998-10-21

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