EP0707686A1 - Machine hydraulique a roues dentees (pompe ou moteur), notamment machine a roues dentees interieures - Google Patents

Machine hydraulique a roues dentees (pompe ou moteur), notamment machine a roues dentees interieures

Info

Publication number
EP0707686A1
EP0707686A1 EP94924212A EP94924212A EP0707686A1 EP 0707686 A1 EP0707686 A1 EP 0707686A1 EP 94924212 A EP94924212 A EP 94924212A EP 94924212 A EP94924212 A EP 94924212A EP 0707686 A1 EP0707686 A1 EP 0707686A1
Authority
EP
European Patent Office
Prior art keywords
pressure field
pressure
sealing plate
housing part
gear machine
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
EP94924212A
Other languages
German (de)
English (en)
Other versions
EP0707686B1 (fr
Inventor
Klaus BUCHMÜLLER
Reinhard Pippes
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.)
Bosch Rexroth AG
Original Assignee
Eckerle Rexroth GmbH and Co KG
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 Eckerle Rexroth GmbH and Co KG filed Critical Eckerle Rexroth GmbH and Co KG
Publication of EP0707686A1 publication Critical patent/EP0707686A1/fr
Application granted granted Critical
Publication of EP0707686B1 publication Critical patent/EP0707686B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

  • Hydraulic gear machine tPu ⁇ roe or otor ⁇ Hydraulic gear machine tPu ⁇ roe or otor ⁇ . in particular internal gear machine
  • the invention is based on a hydraulic gear machine, ie a gear pump or a gear motor, the gear machine being in particular an internal gear machine and having the features from the preamble of claim 1.
  • the pressure field which can be acted upon by the high pressure on the high pressure side of the machine is limited in a plane running perpendicular to the axes of the two gear wheels by a seal which seals the gap between the sealing plate and the housing part.
  • a seal which seals the gap between the sealing plate and the housing part.
  • the aim is to produce a sealing plate in a cost-effective manner by simple stamping and embossing processes. It is difficult to give the sealing plate the shape necessary for the formation of the pressure field. It therefore appears more favorable to provide the pressure field in the housing part adjacent to the sealing plate, which is usually produced as a cast part
  • the invention is based on the object of forming a gear machine with the features from the preamble of claim 1 in such a way that a housing part provided with a pressure field can be used both for a left-handed and a right-handed version.
  • Axes of rotation of the two gearwheels spanned center plane are located, so that there is still a web of the housing part between the two pressure fields.
  • only one of the two pressure fields is delimited by a seal and can be acted upon by the high pressure on the high pressure side of the machine.
  • the second pressure field can only be recognized in that the housing part is intended to also accommodate a seal at a location other than the one currently used.
  • the second pressure field is arranged symmetrically with respect to the central plane with respect to the first pressure field, so that the same conditions are present regardless of the direction of rotation of the machine with respect to the pressure field.
  • the boundary line of the pressure field is partially formed as a circular arc, the center of which lies on the axis of the internally toothed gearwheel designed as a ring gear, and partially designed as a circular arc, the center of which lies on the axis of the externally toothed gearwheel .
  • the pressure field in the area of the tooth engagement of the two gear wheels extends beyond the central plane spanned by the two axes of the gear wheels.
  • a contour section adjoins the median plane towards an outer region of the boundary line designed as a circular arc, the distance from the center point of the circular arc is larger than the radius of the circular arc. This preferably creates a complete area compensation in the tooth meshing area, so that the
  • the housing of the gear machine consists essentially of a middle part, which has a low-pressure connection and a high-pressure connection and closes a chamber with two intermeshing gear wheels in a direction perpendicular to the axes of the gear wheels, and two covers , both of which are symmetrical with respect to a central plane spanned by the axes of the two gear wheels. Then it is possible to build a left-hand rotating version and a right-turning rotating version of a gear machine with the same parts.
  • the middle part is installed in such a way that the other end faces the same cover.
  • Two sealing plates between the covers and the gears are interchanged.
  • the filler pin is mounted in a cover in the central plane.
  • An embodiment according to claim 15 ensures that the operating pressure comes under the seal and thus a very good sealing effect and a very good compensation of the gear wheel side onto a sealing plate acting force is achieved. Because of the individual projections on the inner circumference of the elastomer seal, it is still supported on the inner wall of the groove receiving it when the groove is wider than the actual seal and can therefore be manufactured very economically. When the groove is produced in one machining operation, a machining tool with a diameter corresponding to the larger width of the groove can be used, which results in a higher feed rate.
  • ERSATZBL ⁇ fT (RULE 26) speed allowed.
  • Such wide grooves can also be produced easily without cutting, for example by die casting.
  • Claim 16 relates to a hydraulic gear machine with the two features mentioned.
  • FIG. 1 shows a first exemplary embodiment in a section through the plane spanned by the two axes of the gear wheels
  • FIG. 2 shows a section along the line II-II from FIG. 1,
  • FIG. 3 shows a section along the line III-III from FIG. 1, a cover part of the housing being shown partially in view,
  • FIG. 4 in comparison a pressure field according to FIG. 3 with a conventional pressure field
  • FIG. 5 shows a partial section along the line V-V from FIG. 3,
  • FIG. 6 shows an enlarged view of section VI from FIG. 3,
  • FIG. 7 in the unmounted state, a support ring for an elastomer seal surrounding a pressure field
  • SPARE BLADE (RULE 26) 8 shows a partial section through a second exemplary embodiment lying in a section plane corresponding to FIG. 1, FIG.
  • Figure 9 shows the second embodiment in an axial view from the gears on a sealing plate and a cover part
  • FIG. 10 shows a section along the line X-X from FIG. 9.
  • the internal gear pump shown in FIGS. 1 and 2 has a housing 10 which is composed of an annular middle part 11, which radially encloses a pump chamber 12, a first cover part 13 and a second cover part 14.
  • the two cover parts 13 and 14 limit the pump chamber 12 in the axial direction.
  • the middle part 11 overlaps the two cover parts 13 and 14 in the region of an external recess 15 each.
  • the cover part 13 has a through bore 16 into which a slide bearing 17 is pressed.
  • a flush bore 18 of the cover part 14 is flush with the bore 16 and a slide bearing 17 is also pressed into it.
  • a drive shaft 19 of the pump is mounted in the two slide bearings 17.
  • An externally toothed pinion 20 is fastened within the pump chamber 12 on the drive shaft 19 or is produced in one piece therewith.
  • the pinion is located within an internally toothed ring gear 21, the axis of which is arranged eccentrically to the axis of the pinion 20 and which is mounted on its outer circumference in the central part 11 of the housing 10.
  • the two gearwheels mesh with one another, between which there is otherwise a crescent-shaped free space 23.
  • This free space 23 is approximately half filled by a two-part filler piece 24 which bears against the teeth of the pinion 20 and the ring gear 21 and is supported on a flattened portion of a filler pin 25.
  • This crosses the free space 23 in the center plane 22 and is rotatably mounted in two aligned pocket holes of the cover parts 13 and 14 on both sides of the pump chamber 12.
  • the axial extent of the filler 24 coincides with the axial extent of the two gear wheels 20 and 21.
  • a suction channel 26 and a pressure channel 27 open into the pump chamber 12, the diameter of the suction channel 26 being larger than the diameter of the pressure channel 27.
  • the ring gear 21 has through-holes 28 in the tooth gaps radially from the inside through which a hydraulic fluid can get from the suction channel 26 into the free space 23 and from there into the pressure channel 27.
  • the pump according to FIGS. 1 and 2 is constructed in such a way that the pinion 20, viewed in FIG. 2, must be driven clockwise during operation.
  • the ring gear 21 then also rotates clockwise. Hydraulic fluid located in the tooth spaces travels along the filler piece 24 with the tooth spaces and reaches the tooth engagement area of the two gear wheels. There the hydraulic fluid is displaced through the bores 28 of the hollow wheel 21 into the pressure channel 27. At the same time, hydraulic fluid is drawn into the free space 23 from the suction channel 26 through other bores 28.
  • a good axial sealing of the high-pressure side of the pump is necessary, which can be delimited by an area of the pump chamber 12 in which the filler piece 24 is located and in which the two gearwheels follow the filler piece gradually intertwine.
  • a sealing plate 35 is arranged between the gears 20 and 21 and each cover part 13 or 14, which is pressed axially against the gears 20 and 21 by a pressure field 36 existing between it and the corresponding cover part 13 or 14 .
  • Each sealing plate 35 closely surrounds the shaft 19 and the filler pin 25 and is thereby in a plane perpendicular to the axis of the drive shaft 19 in it Location secured.
  • a pressure field 36 is formed by a recess in the cover part 13 or 14.
  • FIG. 3 it has a semi-crescent shape and extends approximately from the base of the filler piece 24 on the filler piece pin 25 to close to the central plane 22. It is now essential that there is a recess 36 in each cover part 13 or 14 on both sides of the central plane 22, the two recesses 36 of each cover part being mirror-inverted with respect to the central plane 22. Both end at a distance from the central plane 22, so that in their area there is still a web 37 of the respective cover part between the two recesses 36.
  • the outer contour of a recess 36 is essentially formed by four sections, a first section 38 being an arc of a circle, the center of which lies on the axis of the knurling 20.
  • a second section 39 is also a circular arc, the center of which, however, lies on the axis of the ring gear 21.
  • This circular arc 39 merges tangentially towards the central plane 22 into a straight line 40 to be considered as the third section.
  • a section 41 connects the section 38 to the section 40 in the area of the central plane 22.
  • a section 42 connects the arcs 38 and 39 at their widely spaced ends, the section 42 also being partially straight.
  • the outer contour of a pressure field of a known internal gear pump is indicated by a dashed line in FIG. It can be seen that this pressure field extends over the central plane 22, while a pressure field of an internal gear pump according to the invention is limited to one side of the central plane and maintains a distance from the latter in the tooth engagement area. In the known pressure field, the circular arc 39 is continued up to the central plane 22.
  • the reduction of the pressure field in the area of the central plane 22 is approximately compensated for. For the pressurization is therefore in the area of the central plane 22 in approximately the same area is available as in a known internal gear machine, so that a sealing plate 35 is pressed there with approximately the same force against the gears, the same high pressure is required.
  • the two cover parts 13 and 14 of the internal gear pumps shown are designed symmetrically with respect to the central plane 22 not only with regard to the recesses 36, but overall. They can therefore be used for both a left-handed and a right-handed pump.
  • the two versions of a pump can be constructed with the same parts. Only the middle part 11 together with the two sealing plates 35 and the filler 24 is rotated by 180 degrees with the cover parts 13 and 14 about an axis going through the two axes of the gear wheels 20 and 21 and lying in the central plane 22 assembled.
  • the one recess 36 and in the other embodiment the other recess 36 of a cover part is sealed off by a sealing arrangement to form an axial gap between the respective sealing plate 35 and the respective cover part 13 or 14.
  • a groove 43 runs along the edge of each recess 36 to accommodate the sealing arrangement and has the same depth and width over its entire circumference.
  • An elastomer seal 44 is inserted into the groove 43 and, as can be seen in FIG. 5, has a Z-profile cross section with two terminal profile sections 45 and 46 and a central profile section 47.
  • the two terminal profile sections 45 and 46 are perpendicular to the sealing plate 35, the profile section 46 located on the outer wall of the groove 43 being located axially at the bottom of the groove 43 and the profile section 45 located further inside being axially on the
  • the terminal profile section 46 and the middle profile section 47 of the elastomer seal 44 are located completely in the groove 43.
  • the elastomer seal 44 has individual knobs 48 which are spaced apart from one another and are semicircular in an axial view and extend from the inner circumference
  • ERS ⁇ ZBL ⁇ T project from the central profile section 47 and support the elastomer seal 44 on the inner wall of the groove 43.
  • the studs 48 have the bottom of the groove 43 the same distance as the central profile portion 47 radially inside of the tread portion 46.
  • the studs 48 are not directly 46 ver ⁇ connected with the profile portion ⁇ S ⁇ that radially within this an uninterrupted los circumferential pressure surface 49 is present on the elastomer seal 44.
  • Hydraulic fluid flowing from the high pressure side of the pump through bores in a sealing plate 35 into a recess 36 can thus pass between the knobs 48 to the rear of the elastomer seal 44 and pressurize it in the area of the pressure surface 49, so that the elastomer seal 44 depends on of the pressure on the high-pressure side of the pump is pressed against the sealing plate 35 all around with a force of different magnitude.
  • the elastomer seal is supported radially inside and outside in the groove 43, so that it holds its position securely.
  • a support ring 51 made of plastic which has a rectangular cross section and which extends radially outside the first end ⁇ permanent profile section 45 and axially between the central profile section 47 of the elastomer seal 44 and the sealing plate 35 is arranged.
  • the support ring 51 is a so-called open support ring with two ends 52 which overlap relatively far in a straight region of the section 42 of the outer contour of a recess 36 in a plane parallel to the sealing plate 35.
  • Overlapping in a plane parallel to the sealing plate 35 means that if one proceeds in such a plane, one traverses both ends 52. Between the two ends there is therefore no separating joint visible from the inside of a pressure field 36 and running along the support ring.
  • the support ring is of course adapted to the outer contour of a recess 36, so that the two overlapping ends 52 also in the area of a straight section of the Support ring 51 are. Tolerances in the outer circumference of a pressure field and tolerances of the support ring itself can compensate for this because of its open configuration, so that it can rest radially without a gap on the wall of a cover part 13 or 14.
  • two mirror-image elastomer seals 44 are required, one of which is to be inserted into the cover part 13 and the other into the cover part 14.
  • the assignment between cover parts and elastomer seals is exactly the opposite of that of a right-handed pump.
  • the embodiment according to FIGS. 8 to 10 basically has the same structure as the embodiment according to FIGS. 1 to 7. Therefore, only a small part of the pump is shown in the section according to FIG. 8 which corresponds to the section according to FIG. poses.
  • FIG. 9 it can be seen from FIG. 9 that in this embodiment, too, there are two recesses 36 in the cover parts 13 and 14, of which the cover part 14 is shown in FIG. 9, which are symmetrical to one another with respect to the central plane 22.
  • the two recesses 36 have a greater distance from the central plane 22 than the two recesses 36 of the embodiment according to FIGS. 1 to 7 in the region of the tooth engagement of the two gear wheels 20 and 21. This makes the web 37 wider.
  • each cover part 13 or 14 now has a circular recess 60 in the region of the web 37 and at a distance from the recesses 36, which recess lies symmetrically to both sides of the central plane 22.
  • This recess is connected to the high-pressure side via an axial bore 61 in the sealing plate 35 adjacent to the respective cover part, which opens into the recess 60 and extends from a recess 62 on the side face of the sealing plate 35 facing the gearwheels connected to the pump, regardless of whether it is connected to the high-pressure side, whether the pump is driven counterclockwise or clockwise.
  • the sealing plate 35 is assigned to the cover part 14, which is now the cover part (not shown).
  • REAL DATE SHEET (RULE 26) part 13 is adjacent, while the sealing plate 35 shown in FIG. 9 is assigned to the cover part 13.
  • the two sealing plates are symmetrical to one another with respect to the central plane 22, provided that they are viewed next to one another in the direction of the same side facing away from the gearwheels or facing the gearwheels.
  • a sealing plate 35 essentially covers only the high pressure side of a pump, while the low pressure side is kept free, so that there can be no friction between the gears and a sealing plate, which would reduce the efficiency of the pump.
  • Effective in a concrete left-hand or right-hand version of a pump are the pressure field 60 and the pressure field 36, which is hidden in an axial view from the gearwheels by the sealing plate 35. Only these two pressure fields are also with an elastomer seal 63 to the axial gap sealed between the sealing plate 35 and the respective cover part.
  • the elastomer seal is a simple rectangular seal, the axial dimension of which is smaller than the depth of a recess 36 or 60 and which are thus acted upon on the rear side by the pressure prevailing in the pressure field and against the sealing plate 35 can be pressed.

Landscapes

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

Abstract

L'invention concerne une machine hydraulique à roues dentées, notamment une machine à roues dentées intérieures. Une machine connue de ce type comprend deux roues dentées intérieures. Une machine connue de ce type comprend deux engrenages (20, 21) qui s'engrènent dans la chambre d'un carter composé de plusieurs parties, une plaque d'étanchéité (35) placée dans le sens axial, sur les côtés des deux roues dentées, entre ces deux dernierès et une partie du carter, ainsi qu'un champ de pression (36) situé côté haute pression dans ladite partie du carter (13, 14), qui est ouvert en direction de la plaque d'étanchéité et auquel une haute pression peut être appliquée. L'invention vise à produire diverses versions d'une machine à roues dentées qui diffèrent par leur sens de rotation, à l'aide de plusieurs parties identiques. A cet effet, il est prévu qu'un second champ de pression (36) se trouve dans la partie du carter (13, 14), que le premier champ de pression soit uniquement d'un côté et le second champ de pression uniquement de l'autre côté d'un plan médian (22) défini par les axes de rotation des deux engrenages, de manière à ce qu'il subsiste entre les deux champs de pression un morceau (37) de la partie du carter. Dans la version concrète dont le sens de rotation est à gauche ou à droite, la haute pression ne peut être appliquée qu'à un des deux champs de pression. Si la même partie de carter est utilisée dans l'autre version, l'autre champ de pression sert à presser la plaque d'étanchéité contre les roues dentées.
EP94924212A 1993-07-03 1994-06-29 Machine hydraulique a roues dentees (pompe ou moteur), notamment machine a roues dentees interieures Expired - Lifetime EP0707686B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4322240 1993-07-03
DE4322240A DE4322240C2 (de) 1993-07-03 1993-07-03 Hydraulische Innenzahnradmaschine (Pumpe oder Motor)
PCT/EP1994/002114 WO1995002125A1 (fr) 1993-07-03 1994-06-29 Machine hydraulique a roues dentees (pompe ou moteur), notamment machine a roues dentees interieures

Publications (2)

Publication Number Publication Date
EP0707686A1 true EP0707686A1 (fr) 1996-04-24
EP0707686B1 EP0707686B1 (fr) 2000-10-18

Family

ID=6491930

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94924212A Expired - Lifetime EP0707686B1 (fr) 1993-07-03 1994-06-29 Machine hydraulique a roues dentees (pompe ou moteur), notamment machine a roues dentees interieures

Country Status (5)

Country Link
US (1) US5674060A (fr)
EP (1) EP0707686B1 (fr)
JP (1) JP3841823B2 (fr)
DE (2) DE4345273C2 (fr)
WO (1) WO1995002125A1 (fr)

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US6042352A (en) * 1998-08-12 2000-03-28 Argo-Tech Corporation Bearing with pulsed bleed configuration
DE19947884B4 (de) * 1998-10-06 2012-04-19 Denso Corporation Rotationspumpe mit besserer Fluidverschlussstruktur und damit ausgestattete Bremsvorrichtung
DE19847144B4 (de) * 1998-10-13 2006-03-02 Bosch Rexroth Aktiengesellschaft Hydraulische Innenzahnradmaschine
DE19858483A1 (de) 1998-12-18 2000-08-31 Mannesmann Rexroth Ag Hydraulische Verdrängermaschine, insbesondere Verdrängerpumpe
DE19917593C2 (de) * 1999-04-19 2002-05-02 Hydraulik Ring Gmbh Hydraulische Verdrängermaschine
EP1048879B1 (fr) 1999-04-30 2004-06-23 Hydraulik-Ring GmbH Alimentation en fluide sous pression d' une transmission de type CVT
DE10059059A1 (de) * 2000-11-28 2002-05-29 Continental Teves Ag & Co Ohg Innenzahnradpumpe
FR2844312B1 (fr) * 2002-09-05 2006-04-28 Centre Nat Rech Scient Machine tournante a capsulisme
DE102005004657A1 (de) * 2005-02-02 2006-08-03 Eckerle Industrie-Elektronik Gmbh Innenzahnradmaschine
DE102011075415A1 (de) 2011-05-06 2012-11-08 Robert Bosch Gmbh Zahnpumpe
US9163628B2 (en) 2013-03-11 2015-10-20 Imo Industries, Inc. Self adjusting gear pump
WO2016126251A1 (fr) 2015-02-05 2016-08-11 Imo Industries, Inc. Pompe à engrenages internes à croissant indépendante des tolérances
GB2559136B (en) * 2017-01-25 2020-04-15 Edwards Ltd Vacuum pump with biased stator seals and method of manufacture thereof
TR201910917A2 (tr) * 2019-07-22 2019-08-21 Muhammed Veysel Hi̇dromotor
CN117795176A (zh) 2021-08-05 2024-03-29 液压诺德技术有限责任公司 内齿轮机

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Also Published As

Publication number Publication date
JP3841823B2 (ja) 2006-11-08
DE4322240A1 (de) 1995-01-19
DE4345273C2 (de) 1997-02-06
WO1995002125A1 (fr) 1995-01-19
US5674060A (en) 1997-10-07
JPH09503261A (ja) 1997-03-31
EP0707686B1 (fr) 2000-10-18
DE4322240C2 (de) 1997-01-09

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