EP2063126A2 - Machine hydraulique à roue dentée et procédé d'étanchéification d'une machine hydraulique à roue dentée - Google Patents

Machine hydraulique à roue dentée et procédé d'étanchéification d'une machine hydraulique à roue dentée Download PDF

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Publication number
EP2063126A2
EP2063126A2 EP08019578A EP08019578A EP2063126A2 EP 2063126 A2 EP2063126 A2 EP 2063126A2 EP 08019578 A EP08019578 A EP 08019578A EP 08019578 A EP08019578 A EP 08019578A EP 2063126 A2 EP2063126 A2 EP 2063126A2
Authority
EP
European Patent Office
Prior art keywords
gear machine
sealing element
sealing
machine according
housing
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.)
Withdrawn
Application number
EP08019578A
Other languages
German (de)
English (en)
Other versions
EP2063126A3 (fr
Inventor
Sebastian Tetzlaff
Dieter Häcker
Stefan Cerny
Denis Diogo Kluge
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
Priority claimed from DE102008019925A external-priority patent/DE102008019925A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2063126A2 publication Critical patent/EP2063126A2/fr
Publication of EP2063126A3 publication Critical patent/EP2063126A3/fr
Withdrawn legal-status Critical Current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
    • 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
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • 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

Definitions

  • the invention relates to a hydraulic gear machine according to the preamble of claim 1 and a method for sealing a hydraulic gear machine.
  • Gear machines such as external gear pumps or external gear motors, are used in mobile hydraulics for generating or converting hydraulic energy.
  • the main reason for this is their simple structure, which on the one hand leads to good efficiencies and high reliability even under difficult conditions of use and on the other hand allows cost-effective production.
  • Another advantage of the gear machines is that they can be used with a small space and weight requirement in a relatively large speed, temperature and viscosity range.
  • a hydraulic external gear machine having a housing with an interior bounded by two covers attached to the housing.
  • a gear arrangement is arranged with a first and a second gear, which mesh with each other in external engagement.
  • the first gear is mounted on a shaft which is guided on an input / output side to the outside and sealed by an internal shaft seal.
  • the second gear is mounted on an axle.
  • Shaft and axle are mounted via bearing bushes in two opposite arranged in the interior of the housing bearing bodies.
  • a differentiation is made between the front and rear edges of the gears. In gear pumps, the leading edges transmit the rotational motion between the driving and driven gears.
  • the medium to be delivered is conveyed in tooth gaps of the gears from a low pressure side to a high pressure side.
  • flank contact points of the teeth of the gear pair travel along at least one engagement line.
  • the tooth flanks engaging in engagement prevent the pressure medium from flowing back from the high-pressure side to the low-pressure side (sealing effect).
  • gear motors In gear motors, the positive displacement principle of gear pumps is reversed and supplied to the gears pressure medium via an inlet, whereby a torque can be tapped at the outgoing output shaft.
  • the radial sealing of the gears is pressure-dependent in such gear machines by the operating pressure on the high pressure side in the circumferential direction acts on a cog-shaped gap formed between the cogs on the two gears and presses the axis and the shaft of the gears with a pressure-dependent operating force in the bushings.
  • the axial sealing of the gears is pressure-dependent, in each case by the outsides of the arranged on the input / output side and arranged on the opposite side bearing body with pressure, so that the bearing body exert defined contact forces in the axial direction on the side surfaces of the gears, i.
  • the bearing bodies are sealingly pressed on both sides of the gears against the side surfaces of the gears to keep the sealing gap pressure-dependent as small as possible (axial gap compensation).
  • the bearing bodies are mounted axially displaceably on the shaft and axle and have a reduced axial length relative to the housing, so that they are accommodated with axial play in the interior.
  • the bearing bodies have on their outer sides each Axialdruckfelder bounded by partially inserted in grooves of the bearing body and the housing Axialfelddichtonne, wherein a bearing body side bearing surface of the Axialfelddichtung is offset due to the axial play against a housing-side contact surface of the Axialfelddichtung.
  • the pressure acts on the bearing body in the exactly limited Axialdruckfeldern against the internal hydraulic forces, the outer force acting on the bearing bodies force must be slightly larger than the force acting on the bearing body from the inside.
  • a sealing ring is provided in each case, which seals the housing to the outside.
  • the end face of the housing or the cover has a sealing groove in which an elastomer spreads.
  • the present invention seeks to provide a hydraulic gear machine in which the volumetric efficiency is improved with the lowest possible material and manufacturing costs.
  • the inventive hydraulic gear machine consists of a housing, for receiving two intermeshing and mounted in bearing glasses gears.
  • the housing is closed at the end with a lid, between which and the housing, a housing seal and between a low-pressure region and a high-pressure region Axialfelddichtung is provided.
  • This gear machine has an additional sealing element in the region between the housing seal and the low-pressure region.
  • the sealing element consists of a metallic material, since this has good flow and temperature properties.
  • a particularly simple design is achieved when the sealing element is mounted as a raised expression on the lid, and acts on the metallic sealing distance on the housing. If the lid is produced by a casting process, then the sealing element can be produced by a groove in the shaped body. If a very soft material is selected for the sealing element, the sealing element of a new cover can flow into the gap again after disassembly.
  • the sealing element is attached to the housing and flows through the deformation in the gap described.
  • the sealing element may also consist of a harder material, whereby it impresses itself in the softer lid.
  • the sealing element can again emboss in the metallic sealing section of the newly screwed-on cover.
  • the sealing element sits between the housing and the cover as a separate component, and thus imprints into both components, or flows into the gap between the two components.
  • sealing element As close as possible and at least partially parallel to the housing seal.
  • the cross section of the sealing element is made smaller in this area. In areas that are farther away from a screw connection, the cross-section of the sealing element is designed to be correspondingly larger than the sealing gap.
  • the cross section of the sealing element is made round, so that a simple mold is achieved. In other embodiments, but also a square or tapered contour of the sealing element is possible.
  • the sealing element is designed as a wire. This seals the gap particularly well if it consists of a soft material, such as copper.
  • the sealing elements close off at the axial field seals.
  • the sealing elements can either end flush to the Axialfelddichtitch or sealing element and Axialfelddichtung overlap each other.
  • a hydraulic gear machine has a sealing element which has a closed contour along the high and low pressure region and is simply formed as a sealing bead in one piece on the housing or lid.
  • the sealing element acts as a housing seal and additionally seals the low and high pressure areas from each other, whereby, for example, a separate housing seal consisting of a sealing groove and a sealing ring inserted therein no longer necessary and thus the manufacturing and assembly costs is minimized. Leakage in the prior art on the sealing groove from high to low pressure range and can reduce the volumetric efficiency is no longer possible in this embodiment.
  • the sealing element has two sealing projections which rest on the end regions of the axial field seal.
  • cross-section of the sealing element is oval-shaped or pointed, since this is easily deformed during assembly.
  • Adjacent to the side remote from the low and high pressure area side of the sealing element can extend a notch, so when mounting the housing with the cover, the sealing element can flow during deformation in this notch to achieve a uniform surface pressure in the sealing area.
  • a relief groove is formed from this, which leads away from the sealing element to the outside.
  • the gear machine is designed as an external gear machine.
  • a method for sealing a hydraulic gear machine with a housing, for receiving two intermeshing and stored in bearing glasses gears, which is closed with a lid proposed, wherein the gap between the housing and the cover by a screwing together when screwing the system metallic sealing element is sealed.
  • FIG. 1 Viewing direction is in this case from the cover in the direction of the housing 2.
  • the gear machine 1 has an inner space 4 which is bounded by two covers 6 attached to the housing 2.
  • a gear arrangement is arranged in a manner not shown, which has two meshing with each other in external engagement gears.
  • detectable gear shafts 12 are mounted in two oppositely arranged in the interior 4 of the housing 2 each two-piece bearing bodies 14.
  • the bearing body 14 may be executed in one piece in an embodiment not shown.
  • the axial sealing of the gears is pressure-dependent, in each case by the outer sides of the bearing body 14 are acted upon by the operating pressure, so that the bearing body 14 exercise defined, pressure-dependent contact forces in the axial direction on the side surfaces of the gears.
  • the bearing bodies 14 are mounted axially displaceably on the gear shafts 12 and, taking into account the gear width, have a reduced axial length with respect to the housing 2, so that they are received in the interior 4 with axial play.
  • the bearing body 14 have on their outer sides each Axialdruckfelder, which are bounded by partially inserted in grooves of the bearing body 14 about "E" shaped Axialfelddichtungen 16.
  • the pressure acts on the bearing bodies 14 in the exactly limited Axialdruckfeldern against the inner hydraulic forces, the outer force acting on the bearing bodies 14 force must be slightly larger than the force acting on the bearing body 14 from the inside.
  • the force acting on the outside of the bearing body 14 pressure medium is prevented by a metallic sealing section 18, which ensures a plan as possible concern of the lid 6 on the housing 2, from the housing 2 and the cover 6 from the gear machine 1. Furthermore, an additional housing seal 20 prevented in a seal groove 22 in the housing 2 or in a not shown Embodiment in the lid 6 runs, more leaks.
  • the mounted on the outside of the bearing body 14 Axialfelddichtung 16 separates, seen in cross section of the gear machine, the high pressure region 24 from the low pressure region 26th
  • the sealing element 28 prevents the pressure medium via the expanded by the high pump pressure metallic sealing section 18 flows into the sealing groove 22 of the housing seal 20, in which the axial field seal 16 bypasses and flows on the low pressure side 26 as internal leakage again.
  • the seal is made by the sealing element 28 is disposed in the region of the metallic sealing section 18 between the housing 2 and cover 6, whereby the sealing element is deformed when screwing the components together.
  • the displaced material fills the gap forming by component tolerances so that the metallic sealing section 18 on the low-pressure side 26 is reinforced in the area between the ends of the axial field seal 16.
  • FIG. 2 shows the section of a gear machine 1 in the region of the sealing element 28, in which the sealing element 28 is integrally attached to the cover 6, wherein the screw 30 and thus the deformation of the sealing element 28 and the housing seal 20 in the seal groove 22 has not yet taken place.
  • the cross-section 32 of the sealing element 28 is reduced, so that the displaced material spreads in the region of the metallic sealing sections 18.
  • the sealing element 28 is designed as a wire.
  • the sealing element 28 is formed as a closed contour, and thus improves the sealing effect of the metallic Sealing line 18 along its entire length. It is also possible, in addition to or instead of the housing seal 20 and instead of the sealing element 28 to use a sealing means, which is similar to the sealing element 28 with regard to the embodiment. This will be explained in more detail below.
  • FIG. 4 is the inside of the lid 6 off FIG. 3 a gear machine according to a third embodiment with a sealing means or sealing element 34 shown.
  • the sealing means 34 is integrally formed on the cover 6 as a sealing bead and extends approximately along the previous housing seal 20 FIG. 3 around the high and low pressure areas 24, 26 around.
  • FIG. 5a shows in a cross-sectional view along a section line AA FIG. 4 It can be seen that this has an approximately semicircular cross-section and is formed on the cover 6.
  • the sealant 34 has further, see FIG. 4 , Two sealing projections 38, 40 which protrude in approximately between high and low pressure region 24, 26 on the dashed lines indicated axial field seal 16 inwardly.
  • the lid 6 is pressed onto the housing 2, whereby the sealing means 34 in FIG. 4 is plastically and elastically deformed and, as the sealing element 28 in FIG. 1 , sealingly penetrates into the gap formed by component tolerances.
  • the sealing means 34 it is no longer possible, as in the prior art, that pressure medium passes through a sealing groove in the housing 2 or the cover 6 from the high pressure to the low pressure region.
  • the sealing projections 38, 40 By the sealing projections 38, 40, the end portions of the axial field seal 16 are additionally sealed.
  • the function of the housing seal 20 and the sealing element 28 (see FIG. 3 ) is thus adopted by a single sealant 34, whereby the first-mentioned sealing elements are superfluous and the manufacturing cost can be reduced.
  • sealant 34 it does not like designed as an O-ring housing seal 20, can extrude through the sealing gap between the lid 6 and the housing 2.
  • the sealant 34 is produced inexpensively, for example, in aluminum die-casting by a groove in the molding.
  • the sealant 34 in FIG. 4 is formed on the cover 6, but it is quite possible to form this on the housing 2.
  • FIG. 2 shows two variations of the area of the sealant 34 in a cross-sectional view along the section line AA FIG. 4 shown.
  • FIG. 5b In addition to the sealant 34 is a notch 42 immediately adjacent to the high and low pressure region 24, 26, see FIG. 4 , facing away from the sealing edge 44 of the sealant 34 is inserted into the cover 6.
  • the end notch 42 extends along the entire circumference of the sealing means 34. Through this notch 42 is allowed during assembly of the lid 6 and the housing 2 that the sealant 34 can flow in sections during deformation in this notch 42.
  • a relief groove 46 is shown in addition to the end notch 42. This extends from the end notch 42, away from the sealant 34, to the outside. This is thus outside the low and high pressure areas 24, 26, see FIG. 4 , Arranged and can lead to any leaks in the operation of the gear machine 1 in the notch 42 occurring leakage to the outside and relieve this. If the gear machine 1 installed in a tank of an aggregate, so the leakage would be fed directly to the tank. Instead of only one, a plurality of relief grooves 46 may be formed on the notch 42, which open, for example, in a common channel leading to a tank. Another difference of the variation of the area of the sealant 34 in FIG FIG. 5c to FIGS. 5a and 5b is the cross-sectional shape 48 of the sealant 34. This is triangular or pointed and thus can be easily deformed and better penetrate into the housing 2 during assembly.
  • a hydraulic gear machine and a method for sealing a hydraulic gear machine whose housing is closed by a lid, wherein there is a seal between the two components.
  • the sealing effect is supported by a, when screwing together cover and housing, deforming sealing element, which fills the resulting by component tolerances sealing gap.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP08019578.7A 2007-11-22 2008-11-08 Machine hydraulique à roue dentée et procédé d'étanchéification d'une machine hydraulique à roue dentée Withdrawn EP2063126A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007056236 2007-11-22
DE102008019925A DE102008019925A1 (de) 2007-11-22 2008-04-21 Hydraulische Zahnradmaschine und Verfahren zum Abdichten einer hydraulischen Zahnradmaschine

Publications (2)

Publication Number Publication Date
EP2063126A2 true EP2063126A2 (fr) 2009-05-27
EP2063126A3 EP2063126A3 (fr) 2014-03-12

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EP08019578.7A Withdrawn EP2063126A3 (fr) 2007-11-22 2008-11-08 Machine hydraulique à roue dentée et procédé d'étanchéification d'une machine hydraulique à roue dentée

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EP (1) EP2063126A3 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9599106B2 (en) 2009-05-27 2017-03-21 Impact Technology Systems As Apparatus employing pressure transients for transporting fluids
US9803442B2 (en) 2010-06-17 2017-10-31 Impact Technology Systems As Method employing pressure transients in hydrocarbon recovery operations
US9863225B2 (en) 2011-12-19 2018-01-09 Impact Technology Systems As Method and system for impact pressure generation

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19609992B4 (de) 1996-03-14 2005-09-08 Robert Bosch Gmbh Zahnradmaschine

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8707130U1 (de) * 1987-05-18 1988-09-15 Robert Bosch Gmbh, 7000 Stuttgart Zahnradmaschine (Pumpe oder Motor)
DE10109418A1 (de) * 2001-02-27 2002-09-12 Zf Lenksysteme Gmbh Zahnradpumpe
ITBO20010540A1 (it) * 2001-09-07 2003-03-07 Mario Antonio Morselli Perfezionamenti in una pompa volumetrica rotativa
DE102008019925A1 (de) * 2007-11-22 2009-05-28 Robert Bosch Gmbh Hydraulische Zahnradmaschine und Verfahren zum Abdichten einer hydraulischen Zahnradmaschine

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19609992B4 (de) 1996-03-14 2005-09-08 Robert Bosch Gmbh Zahnradmaschine

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9599106B2 (en) 2009-05-27 2017-03-21 Impact Technology Systems As Apparatus employing pressure transients for transporting fluids
US10100823B2 (en) 2009-05-27 2018-10-16 Impact Technology Systems As Apparatus employing pressure transients for transporting fluids
US9803442B2 (en) 2010-06-17 2017-10-31 Impact Technology Systems As Method employing pressure transients in hydrocarbon recovery operations
US9903170B2 (en) 2010-06-17 2018-02-27 Impact Technology Systems As Method employing pressure transients in hydrocarbon recovery operations
US9863225B2 (en) 2011-12-19 2018-01-09 Impact Technology Systems As Method and system for impact pressure generation
US10107081B2 (en) 2011-12-19 2018-10-23 Impact Technology Systems As Method for recovery of hydrocarbon fluid

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Publication number Publication date
EP2063126A3 (fr) 2014-03-12

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