EP0415089B1 - Joint d'étanchéité axial - Google Patents

Joint d'étanchéité axial Download PDF

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Publication number
EP0415089B1
EP0415089B1 EP90114439A EP90114439A EP0415089B1 EP 0415089 B1 EP0415089 B1 EP 0415089B1 EP 90114439 A EP90114439 A EP 90114439A EP 90114439 A EP90114439 A EP 90114439A EP 0415089 B1 EP0415089 B1 EP 0415089B1
Authority
EP
European Patent Office
Prior art keywords
locking ring
axial seal
gap
accordance
ring
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
EP90114439A
Other languages
German (de)
English (en)
Other versions
EP0415089A3 (en
EP0415089A2 (fr
Inventor
Heinz Ing. Teubler
Herbert Ing. Kampf
Erwin Ing. Konz
Klaus A. Ing. Steinert
Roland Ing. Tischler
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.)
Carl Freudenberg KG
LuK Fahrzeug Hydraulik GmbH and Co KG
Original Assignee
Carl Freudenberg KG
LuK Fahrzeug Hydraulik 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 Carl Freudenberg KG, LuK Fahrzeug Hydraulik GmbH and Co KG filed Critical Carl Freudenberg KG
Publication of EP0415089A2 publication Critical patent/EP0415089A2/fr
Publication of EP0415089A3 publication Critical patent/EP0415089A3/de
Application granted granted Critical
Publication of EP0415089B1 publication Critical patent/EP0415089B1/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
    • F04C15/0023—Axial sealings for working fluid

Definitions

  • the invention relates to an axial seal for insertion into an axially aligned groove and for sealing a radially extending gap, in particular the gap between the pressure plate and the housing of hydraulic pumps.
  • suction areas and pressure areas occur in the rotating elements, which are covered by pressure plates and sealed up to a permitted leakage oil level.
  • parts of the back of the pressure plate are under hydraulic pressure, and these high pressure areas often have to be sealed against low pressure areas which are also on the back of the pressure plate.
  • a vane ring with a round cross-section is usually used in vane pumps, alone if the gap to be sealed is not greater than 0.1 mm, or together with a lateral support ring if the gap is in the range of 0.1 mm and 0.5 mm is. Because of the considerable pressure drop in hydraulic pumps, the rubber ring is extruded through the gap when the rubber ring encounters a gap width of more than 0.1 mm.
  • the support ring is arranged laterally to the rubber ring in such a way that it reduces the gap to be sealed, that is to say it forms one from the groove into the gap to be sealed protruding wall, which narrows the local gap width to low pressure, so that the rubber seal there can not be extruded into this low pressure area.
  • the gap is sealed solely by the sealing ring, which is pressed against both the groove base and the machine component opposite the groove.
  • a disadvantage of the previous method of sealing such gaps is the assembly effort for inserting the support ring and the rubber ring into the axially aligned groove.
  • Another disadvantage is that the support ring and the sealing ring are covered when the pump is installed, so that it is not noticed when one of these elements slips out of the groove. The error is only determined during the test run of the pump if it does not reach the necessary pressure.
  • the invention has for its object to provide an axial seal of the type mentioned, which can be easily installed, for example by automatic machines.
  • a locking ring made of extrusion-resistant, but still resilient thermoplastic has a pressure surface running parallel to the gap to be sealed, that a sealing ring made of a rubber-elastic material is arranged on the side of the locking ring opposite the pressure surface, and that locking ring and the sealing ring are permanently connected to one another and have an axial extent which slightly exceeds the groove depth and gap width.
  • the pressure surface rests on the machine part opposite the groove and, as soon as the hydraulic pressure is built up, is pressed more strongly, since the oil in the groove comes under pressure, the sealing ring presses against the groove wall and thus an expanding force generates the good cause of the locking ring protruding wall, which narrows the local gap width to low pressure, so that the rubber seal there can not be extruded into this low pressure area.
  • the gap is sealed solely by the sealing ring, which is pressed against both the groove base and the machine component opposite the groove.
  • a disadvantage of the previous method of sealing such gaps is the assembly effort for inserting the support ring and the rubber ring into the axially aligned groove. Another disadvantage is that the support ring and the sealing ring are covered when the pump is installed, so that it is not noticed when one of these elements slips out of the groove. The error is only determined during the test run of the pump if it does not reach the necessary pressure. From DE-A-344 56 86 a seal for sealing two adjacent surfaces, one of which has a groove, is known, wherein in the groove a sealing part can be attached, the plastically deformable, preferably spaced apart, preferably connected to the sealing part Has pins which are dimensioned such that the sealing part protrudes from the groove in the unmounted state.
  • the seal described here has the disadvantage that due to the U-shaped sealing part in the region of a radially extending gap, the axially extending sealing parts can be easily extruded into the gap because of the considerable pressure drop.
  • the stamped design of the pins already mentioned allows the entire sealing arrangement to slide sideways given the pressure drops to be expected for hydraulic pumps.
  • a seal made of an elastic material is known which interacts with two rigid rings each forming an annular abutment. Because of its construction, this seal is not suitable for sealing radially running gaps under a considerable pressure drop, since the rigid rings mentioned are at best suitable for sealing axially running gaps.
  • the invention has for its object to provide an axial seal of the type mentioned, which can be easily installed, for example by automatic machines.
  • a locking ring made of extrusion-resistant, but still resilient thermoplastic has a pressure surface running parallel to the gap to be sealed, that a sealing ring made of a rubber-elastic material is arranged on the side of the locking ring opposite the pressure surface, and that locking ring and the sealing ring are permanently connected.
  • thermoplastic of the locking ring is on the one hand so resiliently deformable under the pressure that it adapts to the roughness of the component opposite the groove, on the other hand so tight that it is not extruded through the gap to be sealed. In any case, this applies up to a gap width of 0.4 mm, which allows generous tolerances of the pump components and thus lower manufacturing costs.
  • this can be reinforced by fibers which are inserted in the thermoplastic. Glass fibers as a reinforcement have proven particularly useful.
  • the pressure surface of the locking ring should be at least as large as the cross-sectional area of the sealing ring in planes parallel to the gap to be sealed. Such dimensions favor the build-up of hydraulic pressure on the back of the locking ring.
  • the groove is thus largely filled by the sealing ring, which, however, leaves space for high-pressure oil penetrating into the groove, while the thinner locking ring is pressed like a piston against the component opposite the groove and blocks the sealing gap.
  • the locking ring has a thickness that exceeds the gap width and is supported on the groove edge adjacent to the gap on the low-pressure side.
  • the new axial seal can be made by punching out a two-layer material, the first layer contains the high-strength thermoplastic and optionally the fiber insert and the second layer contains the rubber-elastic material.
  • the axial seal can also be assembled from a separately produced locking ring and sealing ring by gluing them together in pairs or vulcanizing them together.
  • Fig. 1 shows a vane pump provided as a power steering pump in a combined, horizontal and vertical longitudinal section. Below the machine axis 1-1, the cutting plane runs horizontally with the exception of the pump outlet 2, and above the axis 1-1, the cutting plane is vertical.
  • a pot-shaped pump housing main part 3 and a pump housing cover 4 are provided, which are screwed together in a sealed manner and enclose a cavity 3a in which a pump package 5 is accommodated.
  • the pump package 5 contains a rotor 6 with vanes 7 guided in slots, a lifting ring 8, a pressure plate 9 and a wear plate 10, which are held together by pins 11, with a fixing to the pump housing cover 4 optionally taking place.
  • the rotor 6 is driven by a shaft 12.
  • a pressure chamber 13 which continues in the direction of the axis 1 into a valve chamber for receiving a valve 14 which is designed as a combined flow control and pressure limiting valve.
  • a Valve spring 15 urges valve 14 against the back of pressure plate 9 with a force of approximately 46 Newtons.
  • a vertical or slightly inclined supply channel 17 leads from a storage container 16 into a knee-shaped curved intake channel 18, which leads to an opening 20 in the pressure plate 9. Since the thickness of the pump package 5 in the axial direction is necessarily a small amount less than the dimension of the interior 3a of the pump housing 3, there is a gap 21 between the bottom surface 22 of the pump housing 3 and the rear side 24 of the pressure plate 9. This gap 21 has one axial width of 0.1 to 0.4 mm and connects the pressure area 13 with the suction area 18, 20 and must therefore be sealed. For this purpose, an axial seal 30 surrounding the suction channels 18, 20 is provided, which is accommodated in an annular groove 25 of the pressure plate 9. The annular groove could just as easily be provided in the pump housing 3.
  • the gap 21 has a pressure-side area 21a and a suction-side area 21b, which are sealed off from one another by means of the seal 30. Accordingly, there is a pressure-side groove flank 26 and a suction-side flank 27, which are connected to one another via the groove bottom 28.
  • the axial seal 30 consists of a locking ring 31 and a sealing ring 41, which are integrally or integrally connected to one another.
  • a pressure surface 32 or a connecting surface 34 of the locking ring each run parallel to the boundary surfaces 22, 24 of the gap 21, and side surfaces 36 and 37 of the locking ring 31 run parallel to the groove flanks 26, 27.
  • the boundary surfaces of the sealing ring 41 are side surfaces 46, 47 or connecting surface 44 and pressure surface 48 have been designated.
  • the thickness of the locking ring 31 is less than that of the sealing ring 41, while the dimension in Direction of the gap are approximately the same or that of the sealing ring is a little less.
  • the minimum thickness of the locking ring 31 depends on the width of the gap 21, which must be covered well, with a certain protrusion from the surface 27 still being required.
  • the locking ring With a sealing gap width of approximately 0.4 mm, the locking ring has a thickness of approximately 1 mm.
  • Locking ring and sealing ring taken together have a thickness which is slightly greater than the depth of the groove 25 and the width of the gap 21, so that in the installed state there is a compression of 20 to 30% of the sealing ring 41.
  • With a width of the sealing ring 41 of 1.8 mm and a height of 2 mm there is a contact pressure of approximately 380 Newtons, with which the surface 32 of the locking ring 31 rests on the surface 22 of the pump housing.
  • the hydraulic pressure penetrates into the groove 25 via gaps and urges the sealing ring 41 against the groove surface 27, which lies on the lower pressure side of the gap 21.
  • the level of the pressure can fluctuate greatly during operation.
  • the deformability of the sealing ring 41 leads to a pressure effect similar to that of a liquid, i.e. H. the locking ring 31 is pressed against the surface 22 with a force corresponding to the size of the surface 34.
  • the surface 22 has the usual processing roughness, so that - in order to achieve a sealing effect - the locking ring 31 on its surface 32 must show a certain degree of flexibility in order to envelop grooves and elevations in the surface 22.
  • the flexibility of the locking ring 31 must not be so great that it is extruded through the gap 21.
  • the locking ring 31 must have a core strength which allows it to withstand the considerable hydraulic pressures, while the surface must be sufficiently soft to adapt to the roughness of machine components.
  • Thermoplastic which can be selected with the necessary properties, are suitable as the material of the locking ring.
  • polytetrafluoroethylene is suitable, its core strength through inserted fibers. for example glass fibers, can be increased so that the axial seal according to the invention withstands considerable pressures of, for example, 240 bar and above.
  • PTFE is known to deform permanently after a certain load, which is referred to as creep or cold flow. This property is not undesirable here, because the surface of the locking ring can adapt to the unevenness of the metallic counter surfaces.
  • PTFE is also easily vulcanizable with rubber materials, so that it can be expected that the sealing ring will not come loose from the locking ring during operation despite shear stress.
  • PTFE can also be filled with other materials such as carbon, graphite, molybdenum sulfide or bronze to increase the resistance to cold flow.
  • Ethylene-tetrafluoroethylene copolymer can also be used as a material for the locking ring, especially since this material is easy to process.
  • Polyterephthalate is also well suited for the intended purpose, since it can be easily vulcanized with the sealing ring.
  • polyamides with or without a glass fiber insert are also suitable for the intended purpose, in particular of quality level PA 6.6, since the tough, hard material structure means that hardly any cold flow can be expected under the pressures to be expected and that the sealing ring also has good vulcanizability.
  • the first layer of which is the thermoplastic and, if appropriate, the Contains fiber insert and the second layer consists of rubber-elastic material.
  • the desired outline shapes are punched out of this two-layer material, a punched cross-sectional shape with pillow-shaped flanks resulting from the resilient, rubber-elastic material, as shown in FIG. 2.
  • the axial seal from separately produced locking rings and sealing rings which are glued or vulcanized to one another along their connecting surface 34 or 44 or - if the requirements are less - are glued.
  • Other thermoplastics are also considered for the locking ring, which will be selected depending on the other requirements at the place of use (temperature resistance, chemical resistance, mechanical abrasion resistance).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Sealing Devices (AREA)
  • Mechanical Sealing (AREA)
  • Gasket Seals (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (10)

  1. Joint d'étanchéité axial destiné à être inséré dans une rainure (25) orientée axialement et à étancher une fente (21) s'étendant radialement, en particulier la fente (21) entre une plaque de pression (9) et un carter (3) d'une pompe hydraulique, joint qui possède une structure en deux parties ayant une étendue axiale qui dépasse la profondeur de la rainure, caractérisé en ce que le joint d'étanchéité axial comporte une bague d'arrêt (31) faite d'une matière thermoplastique qui résiste à l'extrusion, mais est flexible sur une face d'appui (32) s'étendant parallèlement à la fente (21) à étancher, sur le côté (34) opposé à la face d'appui (32) de laquelle est disposée une bague d'étanchéité (41) faite d'un matériau doué d'élasticité caoutchouteuse, et la bague d'arrêt (31) et la bague d'étanchéité (41) sont reliées entre elles de façon durable.
  2. Joint d'étanchéité axial selon la revendication 1, caractérisé en ce que la bague d'arrêt (31) est renforcée par des fibres, incorporées dans la matière thermoplastique, afin d'augmenter la tenue à l'extrusion.
  3. Joint d'étanchéité axial selon la revendication 2, caractérisé en ce que des fibres de verre sont utilisées pour le renforcement.
  4. Joint d'étanchéité axial selon une des revendications 1 à 3, caractérisé on ce que du polytétrafluoroéthylène est utilisé en tant que matière thermoplastique.
  5. Joint d'étanchéité axial selon une des revendications 1 à 3, caractérise en ce qu'un polyamide est utilisé en tant que matière thermoplastique.
  6. Joint d'étanchéité axial selon une des revendications 1 à 5, caractérisé en ce que la face d'appui (32) de la bague d'arrêt (31) est au moins aussi grande que l'aire de section droite de la bague d'étanchéité (41) dans des plans parallèles à la fente (21) à étancher.
  7. Joint d'étanchéité axial selon une des revendications 1 à 6, caractérisé en ce que l'épaisseur de la bague d'étanchéité, (41) dépasse celle de la bague d'arrêt (31) et l'épaisseur de la bague d'arrêt (31) dépasse la largeur de la fente (21).
  8. Joint d'étanchéité axial selon une des revendications 1 à 7, caractérisé en ce que la bague d'arrêt (31) présente une surface relativement souple et un coeur plus ferme.
  9. Joint d'étanchéité axial selon une des revendications 1 à 8, caractérisé en ce qu'il est fabriqué par découpage d'un matériau formé de deux couches dont la première couche contient la matière thermoplastique ainsi que, éventuellement, la charge fibreuse, et dont la seconde couche contient le matériau ayant l'élasticité caoutchouteuse.
  10. Joint d'étanchéité axial selon une des revendications 1 à 7, caractérisé en ce que la bague d'arrêt (31) et la bague d'étanchéité (41) sont fabriquées séparément et sont jumelées du fait qu'elles sont collées ou vulcanisées ensemble.
EP90114439A 1989-07-31 1990-07-27 Joint d'étanchéité axial Expired - Lifetime EP0415089B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3925269 1989-07-31
DE3925269A DE3925269A1 (de) 1989-07-31 1989-07-31 Axialdichtung

Publications (3)

Publication Number Publication Date
EP0415089A2 EP0415089A2 (fr) 1991-03-06
EP0415089A3 EP0415089A3 (en) 1992-01-15
EP0415089B1 true EP0415089B1 (fr) 1994-06-01

Family

ID=6386193

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90114439A Expired - Lifetime EP0415089B1 (fr) 1989-07-31 1990-07-27 Joint d'étanchéité axial

Country Status (3)

Country Link
EP (1) EP0415089B1 (fr)
AT (1) ATE106501T1 (fr)
DE (2) DE3925269A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL9101422A (nl) * 1991-08-23 1993-03-16 Doornes Transmissie Bv Rotatiepomp.
DE4326627B4 (de) * 1993-08-07 2004-10-07 Zf Friedrichshafen Ag Flügelzellenpumpe
DE102005014297A1 (de) 2005-03-24 2006-10-05 Endress + Hauser Gmbh + Co. Kg Gehäuse für ein elektronisches Gerät und Dichtring für ein Gehäuse
DE102015017078B4 (de) 2015-04-17 2019-10-24 Schwäbische Hüttenwerke Automotive GmbH Pumpe
DE102015105933B4 (de) 2015-04-17 2018-04-26 Schwäbische Hüttenwerke Automotive GmbH Pumpe

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2847711A1 (de) * 1978-11-03 1980-05-14 Bosch Gmbh Robert Zahnradmaschine (pumpe oder hydromotor)
GB2086480B (en) * 1980-10-25 1984-01-25 Plessey Co Ltd A rotary positive-displacement pump
US4636155A (en) * 1984-06-29 1987-01-13 Commercial Shearing, Inc. Hydraulic seal having U-shaped gasket and a plurality of plastically deformable posts
CH666102A5 (fr) * 1986-02-18 1988-06-30 Kugler Fonderie Robinetterie Joint d'etancheite.
DE3863235D1 (de) * 1987-05-30 1991-07-18 Bosch Gmbh Robert Reversierbare zahnradmaschine (pumpe oder motor).

Also Published As

Publication number Publication date
DE3925269A1 (de) 1991-02-07
EP0415089A3 (en) 1992-01-15
EP0415089A2 (fr) 1991-03-06
ATE106501T1 (de) 1994-06-15
DE59005901D1 (de) 1994-07-07

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