EP0911524A1 - Pompe à engrenages internes - Google Patents

Pompe à engrenages internes Download PDF

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Publication number
EP0911524A1
EP0911524A1 EP98118622A EP98118622A EP0911524A1 EP 0911524 A1 EP0911524 A1 EP 0911524A1 EP 98118622 A EP98118622 A EP 98118622A EP 98118622 A EP98118622 A EP 98118622A EP 0911524 A1 EP0911524 A1 EP 0911524A1
Authority
EP
European Patent Office
Prior art keywords
internal gear
engine
pinion
pump
sealing
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
EP98118622A
Other languages
German (de)
English (en)
Other versions
EP0911524B1 (fr
Inventor
Dieter Weigle
Klaus Griese
Dietmar Schuchow
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0911524A1 publication Critical patent/EP0911524A1/fr
Application granted granted Critical
Publication of EP0911524B1 publication Critical patent/EP0911524B1/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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels

Definitions

  • the invention is based on a sickle-free internal gear machine according to the preamble of claim 1.
  • Crescentless internal gear machines have engines with an internally toothed ring gear and an externally toothed pinion meshing with this ring gear.
  • This pinion is eccentrically offset from the ring gear and has a toothing with at least one around a tooth lower number of teeth than the toothing of the ring gear.
  • the engine is usually driven or driven via the pinion.
  • Such engines form tooth chambers, which are given a periodic change in volume during operation of the internal gear machine.
  • the tooth chambers pass through a suction, a pressure and two intermediate reversal phases. A pressure medium is thereby transported in the tooth chambers from an inlet on the housing side to an outlet, energy being supplied or withdrawn from the pressure medium, depending on the operating mode of the internal gear machine as a pump or motor.
  • a sickle-free internal gear machine the characterizing features of claim 1 the advantage on that the pressurized surfaces of the sealing elements and thus the forces acting on the sealing elements the pressure angle of the engine are almost constant. This is achieved with sealing elements with a defined sealing edge reached. Apart from the smoothing of the force relationships the load on the sealing elements Sealing elements reduced and thus the life of the internal gear machine elevated. Conversely, can internal gear machines designed in this way with unchanged Use the service life also for higher operating pressures. Further advantages or advantageous developments of the invention result from the subclaims and the description.
  • FIG. 1 shows a cross section through a crescentless internal gear machine
  • Figure 2 the detail is X according to Figure 1, which is a section of the engine at the time the changeover phase from the suction to the pressure phase shows, shown enlarged.
  • the internal gear machine 10 has a housing 11, in the interior thereof an engine 12 is arranged.
  • the engine 12 consists of an internally toothed ring gear 13 with a externally toothed pinion 14 combs.
  • the pinion 14 is eccentric arranged to the ring gear 13 and closes with the ring gear 13 mutually sealed tooth chambers 15 a.
  • the Tooth chambers 15 become in the course of one revolution of the engine 12 issued a periodic volume change, whereby a pressure medium from an inlet 17 to an outlet 18 flows.
  • the inlet 17 and the outlet 18 are on the housing 11 educated.
  • sealing elements 19 arranged in the tooth heads of the ring gear. These sealing elements 19 are supported in the two Reversal phases on the toothing contour of the pinion 14.
  • Figure 2 shows a detail X ( Figure 1) of the engine 12 for Time of changeover from the suction to the pressure phase in an enlarged view.
  • Figure 2 lie a tooth of the pinion 14 and a tooth of the ring gear 13 directly across from.
  • the following description will assumed that the ring gear 13 and the pinion 14th in the direction indicated by the directional arrow D. turn and that in the leading tooth chamber 15.1 higher pressure than in the lagging tooth chamber 15.2 prevails.
  • the leading tooth chamber 15.1 is over a Pressure medium connection 23 connected to a profile groove 20, in which a sealing element 19 is guided in a radially movable manner.
  • a compression spring 24 is arranged in the profile groove 20 on the one hand at the bottom of the profile groove 20 and on the other is supported on the sealing element 19. The preload of the compression spring 24 acts one acting on the sealing element 19 Centrifugal force and presses together with a hydraulic force the sealing element 19 against the toothing of the pinion 14.
  • the sealing element 19 has the shape of the letter J and has a transverse web 25, a shaft 26 and a foot 27. While the crosspiece 25 and the shaft 26 lie inside the profile groove 20, the foot 27 protrudes from the profile groove 20.
  • the shaft 26 has two guide flanks 28, 29 which run parallel to one another and bear against the corresponding wall of the profile groove 20. In order to ensure the radial mobility of the sealing element 19, there is a slight radial play between the shaft 26 and the wall of the profile groove 20.
  • the transverse web 25 of the sealing element 19 forms a stop 30 which is arranged laterally on the guide flank 28 lagging in the direction of rotation D of the ring gear 13 and which has a bevelled rear flank 33.
  • This rear flank 33 interacts with a shoulder 34 of the profile groove 20 and prevents the sealing element 19 from falling out of this profile groove 20.
  • the foot 27 of the sealing element 19 protruding from the profile groove 20 is beveled against the direction of rotation D of the ring gear 13 and forms the pinion on it 14 facing end face from a relatively sharp-edged sealing edge 35.
  • This sealing edge 35 is formed by two rectilinear legs 36, 37 which, with the axis of the sealing element 19 lying in the direction of movement, incline angles W1, W2 of different sizes.
  • the size of the two inclination angles W1, W2 is matched to the contour of the toothing of the pinion 14 in such a way that, at any point in time during the two reversing phases of the engine 12, the inclination angle W3 of a tangent T, which is at the sealing point of the sealing element 19 on the pinion 14 to the contour of this pinion 14 is greater than the angles of inclination W1 and W2 of the legs 36, 37.
  • This requirement ensures that the sealing edge 35 bears against the pinion 14 during the entire reversal phase of the engine 19.
  • the leg 36 lagging in the direction of rotation D is connected to the guide flank 28 via a bevel 38, while the leading leg 37 merges directly into the leading lead flank 29 of the shaft 26. Furthermore, the sealing edge 35 is offset from the trailing leading edge 28 by a distance A in the direction of rotation D forward.
  • the described geometric design of the sealing elements 19 explains itself when considering the hydraulic Conditions on the sealing elements 19 during operation the internal gear machine 10.
  • the geometry of the sealing elements 19 aims at one hand, these sealing elements 19 possible in both reversal phases of the engine 12 press lightly on the pinion 14 in order to minimize wear on the sealing edge 35, on the other hand but the sealing effect of the sealing edge 35 in all operating states to ensure the internal gear machine 10.
  • the hydraulic loading of the sealing elements 19 as quickly as possible to changing operating conditions adjust the internal gear machine 10.
  • a hydraulic counterforce acts on the sealing element 19 opposite.
  • This counterforce consists of one first force component by the area of the high pressure area lying leading leg 37 generated is and a second force component, which by the hydraulic effective area of the lagging in the low pressure area Dental chamber 15.2 lying trailing leg 36 of the sealing element 19 is formed together. Because of the bevel 38 is from the total area of the leg 36 only that by the distance A between the lagging Leading edge 28 and the sealing edge 35 determined Surface section hydraulically effective. Only on this surface section a sealing element 19 there is no pressure equilibrium.
  • the resulting force is therefore the pressure difference between the two tooth chambers 15.1, 15.2 and in size the pressure area of the sealing element defined by the distance A. 19 set.
  • the contact pressure can be reduced of the sealing element 35 on the pinion 14 application-specific adjust over the dimension of the distance A.
  • This Contact force changes its size in the course of one revolution of the engine 12 at most insignificant, since the location of the Sealing edge 35 and thus the area ratios on Sealing element 19 remain largely constant.
  • the measure of the distance A can be between a minimum value and vary a maximum value.
  • the minimum value has been reached if the sealing edge 35 with the trailing guide surface 28 is aligned - in this case there is sealing element 19 hydraulic balance, i.e. towards that Pinion 14 acts only on the force of the compression spring 24 on the sealing element 19 a.
  • the maximum value for the distance A is dependent on the toothing contour of the pinion 14.
  • Essential for the maximum value of the distance A is that the Sealing edge 35 over the entire changeover phase of the engine 12 rests on the pinion 14.
  • Exceeding the maximum value leads to the sealing edge 34 of the contour of the Interlocking of the pinion 14 at least over part of the changeover phase of the engine 12 takes off, which again variable sealing conditions between the pinion 14 and would set the ring gear 13.
  • the sealing element 19 is with its sealing edge 35 at the interdental spaces of the ring gear 13 (Fig.1).
  • the tooth chamber leading in direction of rotation D. 15.1 is already on the pressure medium connection 23 connected to the low pressure side of the internal gear machine 10, while the trailing tooth chamber 15.2 is still under high pressure is acted upon.
  • the one determined by the distance A, not pressure-balanced pressure surface of the sealing element 19 results a force directed away from the ring gear 13 caused by the the sealing element 19 acting centrifugal force is reinforced.
  • the compressive force of the compression spring 24 acts on these two forces opposite.
  • the compression spring 24 is dimensioned so that the amount of compressive force is greater than the centrifugal force and the hydraulic force together. This is the plant of the Sealing element 19 on the ring gear 13 also in this second reversing phase ensured.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP98118622A 1997-10-23 1998-10-01 Pompe à engrenages internes Expired - Lifetime EP0911524B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19746769 1997-10-23
DE19746769A DE19746769C1 (de) 1997-10-23 1997-10-23 Sichellose Innenzahnradmaschine

Publications (2)

Publication Number Publication Date
EP0911524A1 true EP0911524A1 (fr) 1999-04-28
EP0911524B1 EP0911524B1 (fr) 2003-03-26

Family

ID=7846352

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98118622A Expired - Lifetime EP0911524B1 (fr) 1997-10-23 1998-10-01 Pompe à engrenages internes

Country Status (2)

Country Link
EP (1) EP0911524B1 (fr)
DE (2) DE19746769C1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104895781A (zh) * 2014-09-17 2015-09-09 襄阳博亚精工装备股份有限公司 一种内啮合齿轮泵

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3221665A (en) * 1962-01-11 1965-12-07 Hartmann Mfg Co Hydraulic pump or motor with hydraulic pressure-responsive vane
US3279387A (en) * 1964-02-03 1966-10-18 Daniel F Mcgill Reversable pump and motor
EP0545424A1 (fr) 1991-12-06 1993-06-09 J.M. Voith GmbH Pompe à engrenages internes avec joint d'étanchéité incorporé dans les dents
DE4332540A1 (de) * 1993-09-24 1995-03-30 Bosch Gmbh Robert Flügelzellenpumpe
EP0661454A1 (fr) 1993-12-17 1995-07-05 J.M. Voith GmbH Pompe à engrenages internes
EP0686771A2 (fr) * 1994-06-08 1995-12-13 J.M. Voith GmbH Pompe à engrenages internes avec joint d'étanchéité incorporé dans les dents

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK0607497T3 (da) * 1993-01-18 1996-10-21 Voith Gmbh J M Indvendigt fortandet tandhjulspumpe uden segl med tætningselementer indsat i tandhovederne

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3221665A (en) * 1962-01-11 1965-12-07 Hartmann Mfg Co Hydraulic pump or motor with hydraulic pressure-responsive vane
US3279387A (en) * 1964-02-03 1966-10-18 Daniel F Mcgill Reversable pump and motor
EP0545424A1 (fr) 1991-12-06 1993-06-09 J.M. Voith GmbH Pompe à engrenages internes avec joint d'étanchéité incorporé dans les dents
DE4332540A1 (de) * 1993-09-24 1995-03-30 Bosch Gmbh Robert Flügelzellenpumpe
EP0661454A1 (fr) 1993-12-17 1995-07-05 J.M. Voith GmbH Pompe à engrenages internes
EP0686771A2 (fr) * 1994-06-08 1995-12-13 J.M. Voith GmbH Pompe à engrenages internes avec joint d'étanchéité incorporé dans les dents

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104895781A (zh) * 2014-09-17 2015-09-09 襄阳博亚精工装备股份有限公司 一种内啮合齿轮泵

Also Published As

Publication number Publication date
EP0911524B1 (fr) 2003-03-26
DE19746769C1 (de) 1999-02-11
DE59807629D1 (de) 2003-04-30

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