EP3320240A1 - Passage tourant pour un véhicule - Google Patents

Passage tourant pour un véhicule

Info

Publication number
EP3320240A1
EP3320240A1 EP16747724.9A EP16747724A EP3320240A1 EP 3320240 A1 EP3320240 A1 EP 3320240A1 EP 16747724 A EP16747724 A EP 16747724A EP 3320240 A1 EP3320240 A1 EP 3320240A1
Authority
EP
European Patent Office
Prior art keywords
sealing element
sealing
pressure chamber
rotary feedthrough
face
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.)
Ceased
Application number
EP16747724.9A
Other languages
German (de)
English (en)
Inventor
Marc-André SCHÄFER
Horst Brehm
Sebastian NIEDERLE
Robert Heuberger
Andreas Flint
Andre Hofmann
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.)
Schaeffler Technologies AG and Co KG
GAPI TECHNISCHE PRODUKTE GmbH
Original Assignee
Schaeffler Technologies AG and Co KG
GAPI TECHNISCHE PRODUKTE 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 Schaeffler Technologies AG and Co KG, GAPI TECHNISCHE PRODUKTE GmbH filed Critical Schaeffler Technologies AG and Co KG
Publication of EP3320240A1 publication Critical patent/EP3320240A1/fr
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3436—Pressing means
    • F16J15/3448—Pressing means the pressing force resulting from fluid pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60C—VEHICLE TYRES; TYRE INFLATION; TYRE CHANGING; CONNECTING VALVES TO INFLATABLE ELASTIC BODIES IN GENERAL; DEVICES OR ARRANGEMENTS RELATED TO TYRES
    • B60C23/00—Devices for measuring, signalling, controlling, or distributing tyre pressure or temperature, specially adapted for mounting on vehicles; Arrangement of tyre inflating devices on vehicles, e.g. of pumps or of tanks; Tyre cooling arrangements
    • B60C23/001—Devices for manually or automatically controlling or distributing tyre pressure whilst the vehicle is moving
    • B60C23/003—Devices for manually or automatically controlling or distributing tyre pressure whilst the vehicle is moving comprising rotational joints between vehicle-mounted pressure sources and the tyres
    • B60C23/00363—Details of sealings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3404—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal
    • F16J15/3408—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface
    • F16J15/3412—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface with cavities
    • F16J15/342—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member and characterised by parts or details relating to lubrication, cooling or venting of the seal at least one ring having an uneven slipping surface with cavities with means for feeding fluid directly to the face

Definitions

  • the invention relates to a rotary feedthrough for the fluid supply of a pressure chamber, which is arranged between a rotatable component and a stationary fixed component of a vehicle, comprising a seal carrier with at least one channel for fluidic connection to the pressure chamber, wherein at the seal carrier at least two axially spaced sealing rings for static Seal the at least one channel are arranged, and wherein at least one sealing element for axial and radial sealing of the pressure chamber rotationally fixed to the seal carrier is arranged.
  • Rotary feedthroughs are used in particular for trucks and tractors that drive on different surfaces in order to adapt the tire pressure the Fahrpeehigen- shafts. In off-road or on unpaved roads, it is beneficial to have a low tire pressure to increase the vehicle's traction. On paved roads, on the other hand, a higher tire pressure is sought in order to minimize tire wear and fuel consumption.
  • the rotary feedthrough allows a variable adjustment of the tire pressure by increasing or decreasing the air pressure in a compressed air chamber.
  • DE 10 2012 222 339 A1 discloses a fluid rotary feedthrough for sealing a fluid pressure space between a rotatable shaft and a shaft receptacle.
  • the fluid rotary feedthrough comprises a sealing ring carrier and a fitting body, wherein the sealing ring carrier is rotatably and fluid-tightly connected to the shaft or the receptacle and the fitting body bears fluid-tight against the receptacle or the shaft.
  • the fitting body and the sealing ring carrier are at least partially radially spaced from each other spaced to form a fluid pressure space between them.
  • two axially spaced-apart sealing rings are provided, which abut sealingly against the sealing body with a contact surface sealingly against the sealing ring carrier and with a contact surface to seal the fluid pressure chamber on both sides to the outside, and each, preferably independently of each other, relative to the sealing ring carrier and / or the fitting body are rotatable.
  • the sealing ring carrier and the fitting body together form two axially spaced receiving grooves for the sealing rings, the receiving grooves are open to the fluid pressure chamber and each comprise at least one retaining projection which secures the arranged in the receiving groove sealing ring at least partially against a radial position change from the groove to the fluid pressure chamber out ,
  • the respective sealing ring is intended to seal both radially and axially.
  • the respective sealing ring comes into contact axially with a sealing surface.
  • the axial contact pressure of the respective sealing ring on the sealing surface is relatively high, so that due to increased wear and increased heat stress, the life of the respective seal is greatly reduced. At very high pressure loads, the respective seal can also fail immediately.
  • the at least one sealing element comes at a pressure build-up in the pressure chamber axially against a rotatably connected to the rotatable component ring element to the plant, said at least one sealing element has means for reducing the axial contact pressure on the ring member.
  • the means for reducing the axial contact pressure of the at least one sealing element are integrated in the sealing element and thus formed in one piece.
  • the rotary feedthrough entwe- which has a sealing element or particularly preferably two sealing elements.
  • the arrangement of two sealing elements realizes a symmetrical structure of the rotary feedthrough. Consequently, with such a symmetrical construction of the rotary feedthrough, the respective sealing element comes into contact with a respective annular element.
  • the rotary feedthrough is used to connect a tire of a vehicle with a compressed air source.
  • a first end face of the at least one sealing element arranged on the ring element is larger than a second end face of the at least one sealing element adjoining the pressure chamber.
  • the contact pressure which acts on the second end face due to the pressure load in the pressure chamber, distributed to the larger first end face, wherein the amount of axial force acting on the first end face, is just as large like the amount of axial force acting on the second face.
  • the wear on the first end face decreases as well as the heat load between see the second end face and the rotatable ring member.
  • the first end face of the at least one sealing element is at least 1.05 times as large but at most 5 times as large as the second end face of the at least one sealing element.
  • the two faces should have a ratio of 1: 1, 05 to 1: 5, depending on the expected pressures in the pressure chamber.
  • the at least one sealing element has at least one relief bore, which fluidly communicates the pressure chamber. nisch with a back pressure chamber connects.
  • This special design of the at least one sealing element serves in particular as a means for reducing the axial contact pressure. At the same time thereby also a quick concern of the first end face is realized on the ring member.
  • the at least one relief bore is preferably formed axially. When a pressure buildup in the pressure chamber escapes through the at least one relief bore, the compressed air from the pressure chamber in the counter-pressure chamber, whereby a back pressure on the pressure surface of the at least one sealing element which is disposed within the counter-pressure chamber, builds. This counterpressure counteracts the pressure acting on the second end face adjoining the pressure chamber and thereby reduces a contact pressure force of the at least one sealing element on the rotatable ring element.
  • the at least one sealing element has a plurality of relief bores, which fluidly connect the pressure chamber with a counter-pressure space.
  • a variety of relief holes which have a small diameter, favor a slow build-up of the back pressure in the back pressure chamber. Consequently, there is a delayed reduction of the axial contact pressure of the at least one sealing element on the ring element.
  • the invention includes the technical teaching that the at least one sealing element has an axially extending region with a circumferential sealing nose, which comes to bear radially on the seal carrier.
  • the sealing surface between the at least one sealing element and the sealing carrier is less heavily loaded than the sealing surface between the at least one sealing element and the ring element, which also forms a sliding surface. Therefore, it is advantageous to increase the contact pressure at this point, thereby also increasing the reliability of the sealing effect. In particular, this is done by the formation of the circumferential nose on at least one sealing element, which has a particularly small contact surface on the seal carrier and thus undergoes a high contact pressure.
  • the axially extending portion is formed radially flexible.
  • the axially extending region serves as a lever arm for receiving a resulting from the pressure chamber radial force.
  • the axially extending region is at least 0.3 times but at most 0.7 times as large as the total axial dimension of the at least one sealing element. The larger the axially extending region, the larger the lever arm and thus the maximum radial force that can be absorbed.
  • the circumferential sealing nose is arranged substantially statically to the seal carrier.
  • the sealing lug has substantially no relative movement to the seal carrier. However, this does not include slight compensatory movements as well as small axial displacements which permit readjustment of the sealing element, in particular in the case of signs of wear.
  • the axially extending region is preferably larger than the second end face of the at least one sealing element.
  • the axially extending region has a relatively small wall thickness and is thus web-like.
  • the at least one sealing element is made of a
  • FIG. 1 shows a part of a schematic sectional representation to illustrate the structure of a rotary feedthrough according to the invention according to a first embodiment
  • 3 shows a part of a schematic sectional representation to illustrate the structure of a rotary feedthrough according to the invention according to a third embodiment
  • a part of a schematic sectional view to illustrate the structure of a rotary feedthrough according to the invention 4 shows a part of a schematic sectional illustration for illustrating the structure of a rotary feedthrough according to the invention according to a fifth exemplary embodiment
  • FIG. 6 shows a part of a schematic sectional illustration for illustrating the structure of a rotary feedthrough according to the invention according to a sixth embodiment
  • Figure 7 is a part of a schematic sectional view illustrating the construction of a rotary feedthrough according to the invention according to a seventh embodiment.
  • Figures 1 to 7 shows a rotary feedthrough according to the invention for the compressed air supply of a pressure chamber 1, which is arranged between a rotatable component 2 and a stationary fixed component 3 of a - not shown here - vehicle.
  • the rotary feedthrough comprises a seal carrier 4 with a channel 5 for the fluidic connection to the pressure chamber 1.
  • the channel 5 is further connected to another channel 14, which leads to a - not shown - compressed air source.
  • a tire pressure of a - not shown here - tire of the vehicle is set variably and in particular specially tuned to the roadway.
  • two axially spaced sealing rings 6 for static sealing of the channel 5 are arranged on the seal carrier 4, wherein due to the partial sectional view of only one of the two sealing rings 6 is shown.
  • the rotary feedthrough is symmetrical.
  • two sealing elements 7 for axial and radial sealing of the pressure chamber 1 are arranged on the seal carrier 4, wherein only one of the two sealing elements 7 is shown due to the partial sectional view.
  • the respective sealing element 7 comes to bear axially against a respective ring element 8 connected in a rotationally fixed manner to the rotatable component 2.
  • the at least one sealing element 7 has an axially extending region 12 with a circumferential sealing nose 13, which comes to rest radially on the seal carrier 4.
  • a first end face 9a of the sealing element 7 arranged on the ring element 8 is larger than a second end face 9b of the sealing element 7 adjoining the pressure chamber 1.
  • This special design of the sealing element 7 represents a means for reducing the axial contact pressure on the ring element 8.
  • the first end face 9a of the sealing element 7 1, 4 times as large as the second end face 9b of the sealing member 7.
  • the second end face 9b of the sealing member 7 thus serves as a contact surface for the compressed air in the pressure chamber 1, wherein the force acting on the end face 9a on the larger end face 9b is evenly distributed, whereby a contact pressure of the sealing element 7 on the ring element 8 decreases.
  • the first end face 9a of the sealing member 7 is five times as large as the second end face 9b of the sealing member 7. Further, the axially extending portion 12 is formed radially flexible. The axially extending portion 12 is half as large as the entire axial dimension of the seal member 7. In addition, the axially extending portion 12 is larger than the second end face 9 b of the seal member. 7 FIG. 3 shows an embodiment of the sealing element 7 with a first end face 9a, which is twice as large as the second end face 9b of the sealing element 7, wherein the axially extending region 12 is radially flexible.
  • the sealing element 7 has a relief bore 10a which connects the pressure chamber 1 to a counter-pressure space 11 by fluid technology.
  • This special embodiment of the sealing element 7 also represents a means for reducing the axial contact pressure on the ring element 8.
  • the axially extending region 12 is radially flexible and the first end surface 9a is twice as large as the second end surface 9b of the sealing element 7.
  • the sealing element 7 has a plurality of relief bores 10a, 10b, 10c, which connect the pressure chamber 1 to a counter-pressure space 11 by fluid technology.
  • the only means for reducing the axial contact pressure of the sealing element 7 on the ring element 8 are the discharge holes 10a-10c.
  • the axially extending portion 12 is formed radially flexible.
  • FIGS. 6 and 7 illustrate a simplified embodiment of the sealing element 7 from FIG. 5.
  • the sealing element 7 according to FIGS. 6 and 7 has only one relief bore 10a, which fluidly connects the pressure chamber 1 to a counterpressure space 11.
  • the counter-pressure space 1 1 according to FIG. 7 furthermore has a larger volume than the counterpressure space 11 according to FIGS. 5 and 6.

Abstract

L'invention concerne un passage tournant pour l'alimentation en fluide d'une chambre de pression (1) qui est disposée entre une pièce rotative (2) et une pièce fixée de manière stationnaire (3) d'un véhicule, comportant un support (4) de joint d'étanchéité présentant au moins un canal (5) pour la liaison fluidique avec la chambre de pression (1), au moins deux bagues d'étanchéité (6) espacées axialement pour l'étanchéité statique de l'au moins un canal (5) étant disposées sur le support (4) de joint d'étanchéité et au moins un élément d'étanchéité (7) pour l'étanchéité axiale ainsi que radiale de la chambre de pression (1) étant disposé de manière solidaire en rotation sur le support de joint d'étanchéité (4). Selon l'invention, lors d'une montée en pression dans la chambre de pression (1), l'au moins un élément d'étanchéité (7) vient en appui axialement contre un élément annulaire (8) relié de manière solidaire en rotation à la pièce rotative (2), l'au moins un troisième élément d'étanchéité (7) comprenant des moyens de réduction de la pression d'appui axiale sur l'élément annulaire (8).
EP16747724.9A 2015-07-07 2016-07-01 Passage tourant pour un véhicule Ceased EP3320240A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015212641.2A DE102015212641A1 (de) 2015-07-07 2015-07-07 Drehdurchführung für ein Fahrzeug
PCT/DE2016/200304 WO2017005261A1 (fr) 2015-07-07 2016-07-01 Passage tourant pour un véhicule

Publications (1)

Publication Number Publication Date
EP3320240A1 true EP3320240A1 (fr) 2018-05-16

Family

ID=56571098

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16747724.9A Ceased EP3320240A1 (fr) 2015-07-07 2016-07-01 Passage tourant pour un véhicule

Country Status (6)

Country Link
US (1) US10760688B2 (fr)
EP (1) EP3320240A1 (fr)
CN (1) CN107850218B (fr)
BR (1) BR112017027936A2 (fr)
DE (1) DE102015212641A1 (fr)
WO (1) WO2017005261A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017127464A1 (de) 2017-11-21 2019-05-23 Gapi Technische Produkte Gmbh Dichtungsanordnung für eine Drehdurchführung eines Radlager eines Kraftfahrzeugs
DE102017127456A1 (de) 2017-11-21 2019-05-23 Gapi Technische Produkte Gmbh Dichtungsanordnung für eine Drehdurchführung eines Radlagers eines Kraftfahrzeugs
DE102017127438A1 (de) 2017-11-21 2019-05-23 Gapi Technische Produkte Gmbh Radlager zur Lagerung eines Kraftfahrzeugreifens eines Kraftfahrzeugs
DE102017127427B3 (de) 2017-11-21 2019-04-25 Gapi Technische Produkte Gmbh Dichtungsanordnung für eine Drehdurchführung eines Radlagers eines Kraftfahrzeugs
DE102017127432A1 (de) 2017-11-21 2019-05-23 Gapi Technische Produkte Gmbh Dichtungsanordnung für eine Drehdurchführung eines Radlagers eines Kraftfahrzeugs
DE102018100751A1 (de) 2018-01-15 2019-07-18 Schaeffler Technologies AG & Co. KG Radlager zur Lagerung eines Kraftfahrzeugreifens eines Kraftfahrzeugs
DE102018100750B4 (de) 2018-01-15 2022-04-28 Schaeffler Technologies AG & Co. KG Radlager zur Lagerung eines Kraftfahrzeugreifens eines Kraftfahrzeugs
DE102018101411A1 (de) 2018-01-23 2019-07-25 Schaeffler Technologies AG & Co. KG Dichtungsanordnung für eine Drehdurchführung eines Radlager eines Kraftfahrzeugs
DE102020104042B3 (de) 2020-02-17 2021-07-22 Schaeffler Technologies AG & Co. KG Radlager zur Lagerung eines Kraftfahrzeugreifens eines Kraftfahrzeugs

Family Cites Families (13)

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Publication number Priority date Publication date Assignee Title
GB817396A (en) 1956-02-23 1959-07-29 Napier & Son Ltd Seals for sealing rotatable members passing through partitions
GB560280A (en) 1942-11-16 1944-03-28 York Shipley Ltd Sealed joint for rotary shaft
DE3604137A1 (de) 1986-02-10 1987-08-13 Ficht Gmbh Dichtung
DE19963170A1 (de) 1999-12-27 2001-06-28 Leybold Vakuum Gmbh Vakuumpumpe mit Wellendichtmitteln
AU2003232622A1 (en) 2002-05-14 2003-11-11 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydraulic system
JP5615267B2 (ja) * 2009-04-23 2014-10-29 イーグル工業株式会社 メカニカルシール装置
CN201696282U (zh) 2010-05-27 2011-01-05 宁波伏尔肯机械密封件制造有限公司 密封装置
DE202012000209U1 (de) 2012-01-11 2013-04-22 Gapi Technische Produkte Gmbh Fluiddrehdurchführung
CN202901285U (zh) 2012-11-09 2013-04-24 江苏隆达机械设备有限公司 一种随动型侧搅拌机械密封结构
EP2891836B1 (fr) 2013-03-14 2018-11-07 Eagle Burgmann Japan Co., Ltd. Dispositif de joint mécanique
DE102013211529A1 (de) 2013-06-19 2014-12-24 Pfeiffer Vacuum Gmbh Vakuumpumpe
LT2826644T (lt) * 2013-07-18 2018-11-26 Ankol Eood Perdavimo jungtis bent vienam skysčiui perduoti
CN103912685B (zh) 2014-04-15 2016-02-24 清华大学 一种顺逆流泵送结合的径向双端面机械密封装置

Also Published As

Publication number Publication date
US10760688B2 (en) 2020-09-01
US20180195619A1 (en) 2018-07-12
BR112017027936A2 (pt) 2018-08-28
CN107850218A (zh) 2018-03-27
CN107850218B (zh) 2020-12-01
DE102015212641A1 (de) 2017-01-12
WO2017005261A1 (fr) 2017-01-12

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