EP0315878B1 - Pompe à engrènement interne - Google Patents

Pompe à engrènement interne Download PDF

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Publication number
EP0315878B1
EP0315878B1 EP19880118185 EP88118185A EP0315878B1 EP 0315878 B1 EP0315878 B1 EP 0315878B1 EP 19880118185 EP19880118185 EP 19880118185 EP 88118185 A EP88118185 A EP 88118185A EP 0315878 B1 EP0315878 B1 EP 0315878B1
Authority
EP
European Patent Office
Prior art keywords
flanks
pinion
teeth
tooth
internal
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
EP19880118185
Other languages
German (de)
English (en)
Other versions
EP0315878A3 (en
EP0315878A2 (fr
Inventor
Siegfried Hertell
Dieter Otto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Oerlikon Barmag AG
Original Assignee
Barmag AG
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
Priority claimed from DE19873737961 external-priority patent/DE3737961A1/de
Application filed by Barmag AG filed Critical Barmag AG
Publication of EP0315878A2 publication Critical patent/EP0315878A2/fr
Publication of EP0315878A3 publication Critical patent/EP0315878A3/de
Application granted granted Critical
Publication of EP0315878B1 publication Critical patent/EP0315878B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C15/064—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps
    • F04C15/066—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps of the non-return type
    • F04C15/068—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston machines or pumps of the non-return type of the elastic type, e.g. reed 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/088—Elements in the toothed wheels or the carter for relieving the pressure of fluid imprisoned in the zones of engagement
    • 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
    • F04C2/102—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 the two members rotating simultaneously around their respective axes

Definitions

  • Such an internal gear pump is known from DE-OS 34 44 859.
  • This internal gear pump has the peculiarity compared to conventional internal gear pumps that there is a degree of coverage of at least 2, so that the internal gear pump has at least two, but preferably three or more, mutually sealed toothed cells on the suction and printing page forms.
  • the invention has for its object to reduce noise and pressure fluctuations.
  • the solution results from the characterizing part of claim 1.
  • the cutouts can be made, for example, in an end face of the pinion. However, a recess of axially shallow depth is sufficient to ensure that the Torque transmission of the driving flanks can take place without impermissible surface pressure and without impermissible wear.
  • one or more grooves of limited axial length can also be provided in the longitudinal direction of the driving flank, said grooves extending essentially from the head to the foot of the respective tooth.
  • the good hydraulic connection between the leading and the trailing chamber of a double cell also serves if - as further proposed - the driving flanks of the teeth of the pinion (3) (driving flanks of the pinion) and the corresponding counter flanks of the teeth of the ring gear (1) ( Driving flanks of the ring gear) on the suction side of the pump have a lower degree of coverage than the sealing flanks on the pressure side.
  • the degree of coverage of the sealing flanks is preferably equal to or greater than 3, while the degree of coverage of the driving flanks is between 1 and 2. In this way, it is also possible to further reduce the power requirement of the known internal gear pump.
  • the proposed solution includes that the tooth flanks of the pinion and / or the tooth flanks of the ring gear on the driving side and the sealing side are not made mirror-symmetrical. It is essential that the tooth flanks of the driving side have only a relatively small area in which the driving flanks of the pinion and ring gear can come into engagement with one another (engagement area). This meshing area lies - for pinion and ring gear alike - between the pitch circle and the tip circle and begins at the pitch circle.
  • the pressure balance between the chambers of a double cell is also influenced by the rate of pressure rise in the leading cell.
  • This is due to the fact that the tooth cells become very narrow in the area of the dead center and there are very high flow velocities.
  • it is therefore further proposed - preferably in combination with the aforementioned solution - to expand the cross section of the base of the tooth gaps of the ring gear between the root circle and the pitch circle considerably.
  • the bottom of the tooth gap can have an essentially circular cross section in this area.
  • the reduction of the flow velocities and the power consumption caused thereby serves alone or in combination with the other measures of this invention that the outlet openings between the line of engagement and the outer circumference of the ring gear, preferably between the line of engagement and the root circle of the ring gear, are created, with only one towards the line of engagement narrow sealing web is retained.
  • the cross section of the openings is essentially adapted to the cross section of the teeth of the ring gear minus a narrow sealing strip. The cross section of a tooth thus completely covers the outlet opening, but the area of the outlet opening comes as close as possible to the area of the tooth cross section.
  • the outlet openings are guided beyond the base circle of the ring gear and the bottom of the tooth gaps is widened in a funnel shape by a corresponding bevel between the end face and the bottom of the tooth. This also results in a reduction in throttle losses.
  • the pump according to the invention can be designed so that all outlet channels open into a pressure chamber and feed a single hydraulic system. However, several hydraulic systems can also be supplied by grouping the outlet channels in groups, one group being assigned to a separate hydraulic system.
  • the outer wheel 1 is freely rotatably mounted in the housing 31.
  • the outer wheel 1 has an internal toothing 2.
  • the cylindrical housing 31 is closed on both sides by the covers 32 and 33.
  • the shaft 34 is rotatably supported and driven by the motor vehicle engine, not shown.
  • the inner wheel 3 is rotatably mounted on the shaft 34.
  • the shaft 34 is driven by a motor, not shown, for example the internal combustion engine of a motor vehicle.
  • the inner wheel 3 has an external toothing 4, which is in engagement with the internal toothing 2 of the outer wheel 1.
  • the interior of the pump which lies outside the meshing of the teeth, can be filled with a sickle that largely conforms to the tip circles of the gears.
  • the inlet channel 35 see also FIG. 2).
  • the pump forms - as shown in FIG. 1 - on the outlet side between the meshing teeth of the outer wheel 1 and the inner wheel 3 three cells which are closed in the circumferential and axial directions and which have been completely or partially filled with oil via the inlet channel 35.
  • three outlet openings 48.1, 48.3, 48.5 are introduced in the cover 33.
  • Two outlet openings 48.2, 48.4 are introduced into the cover 32.
  • the outlet openings of the cover 33 are arranged offset with respect to the outlet openings of the cover 32. When projected onto a normal plane, the outlet openings in the cover 33 or 32 do not overlap - as shown in FIG. 1.
  • tooth space base 30 represents half the shell of a circular cylinder, the axis of which lies on the plane of symmetry of the tooth space and essentially on the pitch circle or slightly radially outside of the pitch circle 7 of the ring gear.
  • the bottom of the tooth space is again provided with a funnel-shaped extension 26 at both ends.
  • the funnel-shaped extension 26 extends radially to almost the outer circumference of the ring gear.
  • the funnel-shaped extension 26 can also extend in the circumferential direction. However, it is in any case radially outside of the pitch circle 7 of the ring gear 1. If the oil outlet is provided only on one side in a pump according to the invention, the funnel-shaped extension is also only on the relevant side.
  • the check valves on both sides are formed by an n-shaped plate, which is screwed against the wall 53 of the outlet housing 50.
  • the tongues protruding from the common crossbeam 55 of the check valve 54 cover the bores 52. Therefore, these tongues act as check valves.
  • Each check valve only releases the connection from the respective pressure cell formed between the teeth via one of the outlet openings 48, pressure channels 49 and bores 52 if the pressure of the outlet cell is at least equal to the outlet pressure in the outlet chamber 51.
  • the last and smallest pressure cell is directly connected to the outlet chamber via opening 48.5 and corresponding channels 49, 52.
  • an end flank of the pinion is provided with recesses 68.
  • the other flank preferably also has recesses of the same size.
  • the pinion has longitudinal grooves 69 on the tooth base, which extend parallel to the pinion axis. The longitudinal grooves extend over the entire width of the pinion.
  • the recesses 68 extend only over a small part of the width of the pinion. This ensures that the load-bearing capacity of the driving flanks is maintained and the torque transmission is made possible without undue surface pressure and without undue wear.
  • the recess 68 extends here as a partial area of a circle from the base of the longitudinal groove 69 to the head of each pinion tooth.
  • FIG. 2A shows an enlarged view of a tooth flank with a radial section of the pinion through the tooth base.
  • Fig. 1 it can be seen that on the pressure side, the tooth gaps with their sealing flanks form an S-shaped tooth cell.
  • This tooth cell consists of a smaller tooth cell 70 and a larger tooth cell 71.
  • the recesses 68 allow the oil flow that results from this and prevent that different pressures and excessive pressures occur in the channel.
  • the cutouts are only arranged on the driving flanks of the pinion. Therefore, the sealing effect of the sealing flanks is not affected by these recesses.
  • the drive flanks of the ring gear can also have such recesses.
  • a recess 72 is shown only on one of the teeth, it should be noted that the other similar recesses are omitted only to maintain the clarity of the drawing.
  • the recesses on the ring gear must be relatively narrow, so that it is ensured that the teeth of the ring gear completely cover the outlets and a short circuit between successive outlets is avoided.
  • This operating state is maintained at low speeds of the motor vehicle engine.
  • the lubricating oil flow is therefore proportional to the demand according to the speed.
  • the message line can also be used to record other extraordinary operating conditions.
  • the valve 59 serves the purpose of meeting an extraordinary need. It is assumed here that the sum of the oil flow, which is conveyed through throttle 37 on the one hand and via bypass 38 on the other hand, is still throttled and therefore even when the pressure control valve 39 is open, only a partial filling of the cells of the internal toothing takes place at speeds that exceed one certain threshold speed. Fig. 2 meets this requirement in that a further throttle 63 in the bypass 38 is indicated as a symbol.
  • valve 68 which can be switched electromagnetically, for example by the temperature of a machine part will be applied either to the pressure before the throttle 37 or to the pressure behind the throttle 37.
  • the flow velocity of the oil to be pressed out of the tooth space By expanding the base of the tooth space, the flow velocity of the oil to be pressed out of the tooth space, especially in the area shortly before bottom dead center be reduced very strongly.
  • the expansion of the tooth gap of the ring gear can be driven radially outside of the pitch circle 7 until the stability limit of the ring gear is reached.
  • the maximum flow rate when the oil was pressed out was reduced from 20 m / sec to 5 m / sec. This reduction in flow velocity also means a reduction in hydraulic power losses.
  • the same purpose serves on the one hand the funnel-shaped expansion of the tooth space base on the end faces of the ring gear and the corresponding dimensioning of the outlet openings.
  • the fact that the outlet openings are arranged radially outside the line of engagement while maintaining a narrow but sufficient sealing strip ensures that there is no short circuit between successive tooth cells via the outlet openings.
  • this enables the outlet openings to be made over a very large area.
  • the area of the outlet openings is selected so that it is covered by the tooth cross section of the ring gear with sufficiently wide sealing surfaces in the circumferential direction.
  • the outlet openings can be chosen to be very large and the outlet openings can furthermore be arranged with a smaller pitch than the tooth pitch. This ensures that there is always a large connection cross-section between the tooth cells and the outlet.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Claims (8)

  1. Pompe à engrenages intérieurs comportant un pignon menant (3) et une roue à denture intérieure (1), dans laquelle, côté refoulement, les flancs arrières des dents du pignon (flancs d'étanchéité du pignon) engrènent avec les flancs conjugués concernés de la roue à denture intérieure (flancs d'étanchéité de la roue à denture intérieure) dans la zone comprise entre le point d'intersection des cercles de tête et le point primitif avec un rapport de recouvrement égal ou supérieur à 2 de manière telle qu'une pluralité de cellules fermées les unes par rapport aux autres sont formées, plusieurs desdites cellules communiquant chacune par au moins une sortie munie d'un clapet anti-retour avec le conduit de refoulement commun, caractérisé en ce que les flancs menants des dents du pignon (3) (flancs menants du pignon) et/ou les flancs conjugués concernés des dents de la roue à denture intérieure (1) (flancs menants de la roue à denture intérieure) présentent des évidements, rainures ou analogues limités axialement, qui relient la tête des dents au pied des dents..
  2. Pompe à engrenages intérieurs selon la revendication 1, caractérisée en ce que les entredents de la roue à denture intérieure et/ou les entredents du pignon, dans la mesure où ils sont situés à l'extérieur ou à l'intérieur du cercle primitif de fonctionnement, ont une section considérablement agrandie par rapport chaque fois à la courbe enveloppe de l'autre dent.
  3. Pompe à engrenages intérieurs selon l'une des revendications précédentes, caractérisée en ce que les flancs menants des dents du pignon (3) (flancs menants du pignon) et les flancs conjugués concernés des dents de la roue à denture intérieure (1) (flancs menants de la roue à denture intérieure) présentent côté aspiration de la pompe, un rapport de recouvrement plus faible que les flancs d'étanchéité côté refoulement.
  4. Pompe à engrenages intérieurs selon l'une des revendications précédentes, caractérisée en ce que le rapport de recouvrement des flancs d'étanchéité est égal ou supérieur à 3 et en ce que le rapport de recouvrement des flancs menants est compris entre 1 et 2.
  5. Pompe à engrenages intérieurs selon l'une des revendications précédentes, caractérisée en ce que les ouvertures de sortie sont situées entre la ligne d'action et le cercle périphérique de la roue à denture intérieure et s'étendent jusqu'à proximité de la ligne d'action en laissant une étroite surface d'étanchéité.
  6. Pompe à engrenages intérieurs selon l'une des revendications 3 à 5, caractérisée en ce que, sur la face frontale tournée vers les orifices de sortie, le fond des entredents de la roue à denture intérieure est élargi en forme d'entonnoir pratiquement jusqu'à la périphérie de la roue à denture intérieure.
  7. Pompe à engrenages intérieurs selon l'une des revendications précédentes, caractérisée en ce que la roue à denture intérieure compte jusqu'à trois dents, de préférence deux dents, de plus que le pignon.
  8. Pompe à engrenages intérieurs selon l'une des revendications précédentes, caractérisée en ce que le pignon est mené.
EP19880118185 1987-11-07 1988-11-02 Pompe à engrènement interne Expired - Lifetime EP0315878B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19873737961 DE3737961A1 (de) 1987-11-07 1987-11-07 Innenzahnradpumpe
DE3737961 1987-11-07
DE3743153 1987-12-19
DE3743153 1987-12-19

Publications (3)

Publication Number Publication Date
EP0315878A2 EP0315878A2 (fr) 1989-05-17
EP0315878A3 EP0315878A3 (en) 1990-01-17
EP0315878B1 true EP0315878B1 (fr) 1992-04-01

Family

ID=25861598

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19880118185 Expired - Lifetime EP0315878B1 (fr) 1987-11-07 1988-11-02 Pompe à engrènement interne

Country Status (2)

Country Link
EP (1) EP0315878B1 (fr)
DE (1) DE3869737D1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4107704C2 (de) * 1990-03-15 1994-12-01 Barmag Luk Automobiltech Hydraulikpumpe
EP0579981B1 (fr) * 1992-06-29 1996-10-23 LuK Automobiltechnik GmbH & Co. KG Pompe à engrenages internes pour fluide hydraulique
DE19804133A1 (de) * 1998-02-03 1999-08-12 Voith Turbo Kg Sichellose Innenzahnradpumpe
DE102006047312A1 (de) * 2006-10-06 2008-04-10 Sauer-Danfoss Aps Hydraulische Maschine
DE102022130861A1 (de) 2022-11-22 2024-05-23 Klaus Stühmeier Fördereinrichtung für flüssiges oder gasförmiges Medium

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2428181A (en) * 1944-10-27 1947-09-30 Frank C Sibley Rotary gear pump
US2830542A (en) * 1953-06-22 1958-04-15 Gen Motors Corp Fluid pump
US3490383A (en) * 1969-01-29 1970-01-20 Koehring Co Hydraulic pump or motor
DE2240632C2 (de) * 1972-08-18 1983-09-01 Danfoss A/S, 6430 Nordborg Rotationskolbenmaschine für Flüssigkeiten
US4025243A (en) * 1973-01-05 1977-05-24 Gresen Manufacturing Company Orbital device
US4145167A (en) * 1976-02-17 1979-03-20 Danfoss A/S Gerotor machine with pressure balancing recesses in inner gear
DE3444859A1 (de) * 1983-12-14 1985-06-27 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Rotationszellenpumpe fuer hydrauliksysteme
DE3444857A1 (de) * 1984-12-08 1986-06-12 Graubremse Gmbh, 6900 Heidelberg Steuerventil

Also Published As

Publication number Publication date
EP0315878A3 (en) 1990-01-17
DE3869737D1 (de) 1992-05-07
EP0315878A2 (fr) 1989-05-17

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