EP0607497A1 - Pompe à engrenages internes avec joint d'étanchéité incorporé dans les dents - Google Patents

Pompe à engrenages internes avec joint d'étanchéité incorporé dans les dents Download PDF

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Publication number
EP0607497A1
EP0607497A1 EP93114117A EP93114117A EP0607497A1 EP 0607497 A1 EP0607497 A1 EP 0607497A1 EP 93114117 A EP93114117 A EP 93114117A EP 93114117 A EP93114117 A EP 93114117A EP 0607497 A1 EP0607497 A1 EP 0607497A1
Authority
EP
European Patent Office
Prior art keywords
sealing element
ring gear
pinion
internal gear
gear pump
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.)
Granted
Application number
EP93114117A
Other languages
German (de)
English (en)
Other versions
EP0607497B1 (fr
Inventor
Franz Arbogast
Peter Peiz
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.)
JM Voith GmbH
Original Assignee
JM Voith GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by JM Voith GmbH filed Critical JM Voith GmbH
Publication of EP0607497A1 publication Critical patent/EP0607497A1/fr
Application granted granted Critical
Publication of EP0607497B1 publication Critical patent/EP0607497B1/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
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F04C15/0019—Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
    • 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

  • Document (2) describes a radially movable sealing element, which - without requiring excessive manufacturing effort - significantly improves the sealing effect when pressure builds up between the opposing tooth tips of the gearwheels due to the shape.
  • the contour of the sealing element on the one hand and the complementary design of the sealing element and the profile groove in the tooth head on the other hand bring with it some problems.
  • the disadvantage here is that when the dead center is exceeded, the entire system pressure, ie the working pressure generated by the pump, rests on the sealing element. This would be for the purpose of sealing a much lower pressure will suffice.
  • the high system pressure leads to excessive wear of the sealing element.
  • the invention has for its object to design a pump according to the preamble of claim 1 such that not the entire system pressure is used for sealing, but a much lower pressure, which is sufficient for the purpose of sealing.
  • the special design of the sealing element ensures that there is a minimal gap between the pinion head and the ring gear head.
  • the volumetric efficiency can be improved, which in turn means that the internal gear pump can also be used for higher pressures.
  • the elaborate and complicated profile grinding of the hollow head shape is eliminated when producing the ring gear, because the sealing elements can be produced separately therefrom.
  • FIG. 1 shows in a cross section a sickle-free, head-sealing and backlash-type internal gear pump, each sealing with a flank, in the area of a central housing part, which - viewed in the axial direction - is followed by further housing parts.
  • An externally toothed pinion 5 fastened on a pinion shaft 4 is in engagement with an internally toothed ring gear 6.
  • the toothing 12 of the pinion 5 and the ring gear 6 has an axial width which is greater than the pitch circle diameter of the pinion.
  • the pinion 5 and the ring gear 6 are not mounted coaxially, but eccentrically to one another; furthermore, the pinion 5 has one tooth less than the ring gear 6, so that in each case the outside of a tooth head 13 on the pinion 5 comes into contact with the inside of a tooth head 14 on the ring gear 6.
  • a suction connection 7 can also be seen in the zone in which the teeth on the pinion 5 or ring gear 6 disengage when rotated in the direction of the arrow X.
  • the suction connection 7 in the middle part of the housing, in which the ring gear 6 and the pinion 5 are mounted, is followed in the axial direction by a suction pocket, which extends over part of the outer surface 20 of the ring gear 6, to the adjacent housing parts.
  • a pressure connection 10 is located, also starting from one over a peripheral area Ring gear 6 extending pressure pocket on the opposite side of the pump.
  • FIG. 2 shows a section of the ring gear 6 in the region of a tooth head 14.
  • the openings (radial bores) 17 provided for the inflow of the pressure medium to the interior of the internal gear pump are machined in the tooth gaps. While in the construction according to the main patent these openings 17 each cut the profile groove 34 for the sealing elements 30 and thus always act on the back of the sealing element 30 with the pressure prevailing in the leading tooth gap, the openings 17 no longer cut the profile grooves 34.
  • the design change also has functional advantages. While in the construction according to the main patent, the (contact) pressure effective on the back of the sealing element 30 is always as great as the pressure in the leading tooth gap (which means that the sealing element with the force corresponding to the system pressure in the area of reversal from the suction side to the pressure side the pump is pressed outwards), the pressure acting on the sealing element 30 is only a partial pressure due to the design change. In a particularly advantageous manner, this partial pressure effective on the back of the sealing element can be achieved by means of - cf. 3 - along the sealing elements 30 provided bores 30 'or by means of - see. Fig.
  • the partial pressure mentioned - in conjunction with the present improvement invention - also ensures that the sealing element 30 in the area of the pressure build-up (after the so-called dead center TP at the transition from the suction to the pressure space - see also reference symbol "A" / FIG. 1) is moved against the pinion head and comes to rest here.
  • the bores 30 '(and also the grooves 30'') connect the free space (groove space) of the profile groove 34 at the foot of the sealing element 30 in each case - viewed in the direction of rotation X before the dead center TP between the Suction chamber and pressure chamber - with the leading tooth gap; as soon as the dead center TP is exceeded, the bores 30 '(and the grooves 30'') connect the mentioned groove space with the (lagging) tooth gap lying behind it.
  • the sealing element 30 is provided with an allowance E in terms of construction or production technology in order to be able to compensate for any manufacturing tolerances.
  • the sealing element 30 can slide radially out of or into the profile groove 34 (arrow Y) by the allowance E mentioned compared to the theoretical tip circle diameter K of the tooth tip 14 of the ring gear 6, the two end positions by the inner collar of the mushroom cap of the sealing element 30 on the one hand and by a positive connection (fixed stop) between the foot of the sealing element 30 and a wall of the profile groove 34 on the other hand.
  • the sealing element 30 is always by means of a corrugated spring up to the abovementioned stop between the foot part of the sealing element 30 and the corresponding wall of the profile groove 34 pressed outwards.
  • the sealing element 30 is ultimately always in its position opposite the profile groove 34.
  • this now means that the theoretical tip circle diameter on the ring gear 6 necessary for a trouble-free operation is reduced by the aforementioned inlet allowance E on the sealing element 30. This reduction can now lead to faults at the moment of the first contact between the ring gear 6 and the pinion 5 (cf. "A" in FIG. 1).
  • the above-mentioned corrugated spring is dispensed with, so that after the sealing element 30, due to the centrifugal force, always in the profile groove 34, i.e. is pressed into the tooth tip 14, the tip circle diameter K is larger than the theoretical tip circle diameter. Since the theoretical beginning of the tooth tip seal is still in the suction space (cf. "A" in FIG. 1), but the sealing element 30 is pressed outwards as a result of the centrifugal force, there can be no contact between the two gear wheels. As already mentioned, the tooth tip seal is therefore only built up when the partial pressure acts on the sealing element 30.
  • the fixed stop for the sealing element 30 is realized in connection with the non-load-bearing flank F 2, and this new geometry thus ensures sufficient strength for the forces that occur.
  • the tooth cross section on the side of the load-bearing flank F 1 in the area of the profile groove 34 for receiving the sealing element 30 thus corresponds to a bending beam with the same bending stress.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP93114117A 1993-01-18 1993-09-03 Pompe à engrenages internes avec joint d'étanchéité incorporé dans les dents Expired - Lifetime EP0607497B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4301104 1993-01-18
DE4301104 1993-01-18

Publications (2)

Publication Number Publication Date
EP0607497A1 true EP0607497A1 (fr) 1994-07-27
EP0607497B1 EP0607497B1 (fr) 1996-06-12

Family

ID=6478363

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93114117A Expired - Lifetime EP0607497B1 (fr) 1993-01-18 1993-09-03 Pompe à engrenages internes avec joint d'étanchéité incorporé dans les dents

Country Status (7)

Country Link
US (1) US5451150A (fr)
EP (1) EP0607497B1 (fr)
JP (1) JPH06241174A (fr)
AT (1) ATE139305T1 (fr)
DE (1) DE59302915D1 (fr)
DK (1) DK0607497T3 (fr)
ES (1) ES2090799T3 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0661454A1 (fr) * 1993-12-17 1995-07-05 J.M. Voith GmbH Pompe à engrenages internes
DE4419975A1 (de) * 1994-06-08 1995-12-14 Voith Gmbh J M Sichellose Innenzahnradpumpe mit in die Zahnköpfe eingesetzten, rückseitig über Druckkanäle angesteuerten Dichtelementen
DE19746769C1 (de) * 1997-10-23 1999-02-11 Bosch Gmbh Robert Sichellose Innenzahnradmaschine
EP0933530A1 (fr) * 1998-02-03 1999-08-04 Voith Turbo GmbH & Co. KG Pompe à engrenages internes sans croissant
EP0933529A3 (fr) * 1998-02-03 2000-06-07 Voith Turbo GmbH & Co. KG Pompe à engrenages internes sans croissant

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6273695B1 (en) * 1999-03-26 2001-08-14 Voith Turbo Gmbh & Co. Kg Sickleless internal gear wheel pump with sealing elements inserted into the tooth tips
DE102020001287A1 (de) 2020-02-27 2021-09-02 Hypneu Gmbh Hydraulik Und Pneumatik Anordnung zur axialen Abdichtung eines Zahnrades entlang der Zahnflanke und des Zahngrundes gegenüber eines verschieblichen Negativbauteils

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB793089A (en) * 1956-06-09 1958-04-09 Hanomag Ag Improvements in rotary engines and compressors
US2866417A (en) * 1956-06-11 1958-12-30 Hanomag Ag Rotary piston machine
US3429269A (en) * 1965-08-21 1969-02-25 Concentric Eng Ltd Fluid pumps and motors
DE4104397A1 (de) * 1990-03-09 1991-09-12 Voith Gmbh J M Innenzahnradpumpe
DE4140293A1 (de) * 1991-12-06 1993-06-09 J.M. Voith Gmbh, 7920 Heidenheim, De Sichellose innenzahnradpumpe mit in die zahnkoepfe eingesetzten dichtelementen

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US726896A (en) * 1901-11-23 1903-05-05 Pontus Erland Fahlbeck Rotary engine.
US748348A (en) * 1902-06-16 1903-12-29 Cooley Epicycloidal Engine Dev Company Rotary fluid-engine.
US3758243A (en) * 1972-04-24 1973-09-11 Gen Motors Corp Rotary machine apex seal
DE3633330A1 (de) * 1986-10-01 1988-04-07 Pierburg Gmbh Drehkolbenmaschine
CH682939A5 (de) * 1990-03-09 1993-12-15 Voith Gmbh J M Innenzahnradpumpe.

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB793089A (en) * 1956-06-09 1958-04-09 Hanomag Ag Improvements in rotary engines and compressors
US2866417A (en) * 1956-06-11 1958-12-30 Hanomag Ag Rotary piston machine
US3429269A (en) * 1965-08-21 1969-02-25 Concentric Eng Ltd Fluid pumps and motors
DE4104397A1 (de) * 1990-03-09 1991-09-12 Voith Gmbh J M Innenzahnradpumpe
DE4140293A1 (de) * 1991-12-06 1993-06-09 J.M. Voith Gmbh, 7920 Heidenheim, De Sichellose innenzahnradpumpe mit in die zahnkoepfe eingesetzten dichtelementen

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0661454A1 (fr) * 1993-12-17 1995-07-05 J.M. Voith GmbH Pompe à engrenages internes
DE4419975A1 (de) * 1994-06-08 1995-12-14 Voith Gmbh J M Sichellose Innenzahnradpumpe mit in die Zahnköpfe eingesetzten, rückseitig über Druckkanäle angesteuerten Dichtelementen
DE19746769C1 (de) * 1997-10-23 1999-02-11 Bosch Gmbh Robert Sichellose Innenzahnradmaschine
EP0933530A1 (fr) * 1998-02-03 1999-08-04 Voith Turbo GmbH & Co. KG Pompe à engrenages internes sans croissant
EP0933529A3 (fr) * 1998-02-03 2000-06-07 Voith Turbo GmbH & Co. KG Pompe à engrenages internes sans croissant
US6095782A (en) * 1998-02-03 2000-08-01 Voith Turbo Gmbh & Co Kg Crescentless internal gear pump
US6164943A (en) * 1998-02-03 2000-12-26 Voith Turbo Gmbh & Co., Kg Internal geared wheel pump without crescent-shaped [sickle] piece

Also Published As

Publication number Publication date
ATE139305T1 (de) 1996-06-15
DK0607497T3 (da) 1996-10-21
EP0607497B1 (fr) 1996-06-12
US5451150A (en) 1995-09-19
DE59302915D1 (de) 1996-07-18
ES2090799T3 (es) 1996-10-16
JPH06241174A (ja) 1994-08-30

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