WO2017102081A1 - Joint d'étanchéité d'arbre radial et procédé permettant de rendre étanche une pièce tournante de machine au moyen d'un joint d'étanchéité d'arbre radial - Google Patents

Joint d'étanchéité d'arbre radial et procédé permettant de rendre étanche une pièce tournante de machine au moyen d'un joint d'étanchéité d'arbre radial Download PDF

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Publication number
WO2017102081A1
WO2017102081A1 PCT/EP2016/002112 EP2016002112W WO2017102081A1 WO 2017102081 A1 WO2017102081 A1 WO 2017102081A1 EP 2016002112 W EP2016002112 W EP 2016002112W WO 2017102081 A1 WO2017102081 A1 WO 2017102081A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft seal
radial shaft
machine part
sealing lip
sealing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2016/002112
Other languages
German (de)
English (en)
Inventor
Matthias Palmer
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.)
Kaco GmbH and Co KG
Original Assignee
Kaco 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 Kaco GmbH and Co KG filed Critical Kaco GmbH and Co KG
Priority to CN201680080233.4A priority Critical patent/CN108700197A/zh
Publication of WO2017102081A1 publication Critical patent/WO2017102081A1/fr
Anticipated expiration legal-status Critical
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
    • F16J15/164—Sealings between relatively-moving surfaces the sealing action depending on movements; pressure difference, temperature or presence of leaking fluid
    • 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
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3208—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip provided with tension elements, e.g. elastic rings
    • F16J15/3212—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip provided with tension elements, e.g. elastic rings with metal springs
    • 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
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/322—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip supported in a direction perpendicular to the surfaces
    • 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
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3228—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip formed by deforming a flat ring

Definitions

  • the invention relates to a radial shaft seal according to the preamble of claim 1 and to a method for sealing a rotating machine part with such a radial shaft seal according to the preamble of claim 15.
  • the sealing lip is always on the rotating machine part, thereby ensuring the seal. Due to the friction between the sealing lip and the rotating machine part occur high friction losses. They also lead to the sealing element is subject to appropriate wear.
  • the invention has the object of providing the generic radial shaft seal and the generic method in such a way that the friction losses can be kept low.
  • the radial shaft seal according to the invention is characterized in that it is provided with the centrifugal force elements. They form a centrifugal force mechanism, which ensures that the centrifugal elements then, when they assume their radially inner position, press the sealing lip against the stationary machine part, so that a secure seal is ensured when the machine part is at rest. If the machine part rotates, then the centrifugal force elements are adjusted outward by means of centrifugal force via the carrier connected non-rotatably to the machine part, so that the load on the sealing lip is correspondingly reduced.
  • the centrifugal force elements can be designed so that the sealing lip from at least idling speed rotating machine part either only with very little force applied to the machine part or even lifted off her, so that no contact between the sealing lip and the rotating machine part takes place.
  • centrifugal elements are annular and arranged so that they surround the sealing lip over the entire circumference.
  • the carrier or the centrifugal force elements are advantageously provided with at least one radially extending slot, in each engages a pin of centrifugal elements or the carrier.
  • the pins ensure the torque entrainment of centrifugal elements when the machine part is rotated with the rotatably mounted on him carrier. In the radially extending slots, the pin and thus the respective centrifugal force element can move reliably in the radial direction.
  • the centrifugal elements are loaded radially inwardly in a preferred embodiment by at least one annular spring.
  • the annular spring surrounds the centrifugal elements.
  • the centrifugal elements can be reliably adjusted in the radial direction, they are axially secured by at least one securing part.
  • the centrifugal elements can thus not be adjusted axially relative to the rotating machine part.
  • the centrifugal elements between the carrier and the securing part are arranged axially secured. In this way, it is ensured in both axial directions that the centrifugal elements do not move unintentionally axially.
  • the securing part is a retaining ring which is coaxial with the axis of the radial shaft seal.
  • the carrier is a coaxial with the axis of the radial shaft seal lying ring.
  • the carrier has a Z-shaped cross-section. Due to this cross-sectional configuration, the carrier has a radially inner and a radially outer ring. With the radially inner ring, the carrier can very easily be secured against rotation on the machine part. With the radially outer ring, it is possible to surround the securing part for the centrifugal elements outside and thus protect.
  • the carrier is part of a transmitter wheel.
  • the rotating machine part is part of an internal combustion engine with automatic start-stop.
  • the encoder wheel is in this case part of a rotary encoder with which the speed and the rotational position of the machine part can be reliably detected. If the machine part is to be turned from standstill again, the motor control knows, based on the signals of the sender wheel, which position the stationary machine part occupies.
  • the carrier protrudes axially from a housing of the radial shaft seal.
  • This housing is advantageously used to secure the sealing element within the radial shaft seal.
  • the security part can be better protected, for example, from contamination or deposits of dirt particles contained in the medium to be sealed.
  • sealing element is a sealing washer. Then the sealing lip is formed by the radially inner, elastically bent part of the sealing disc.
  • the sealing washer is made of PTFE.
  • the sealing lip is pressed by the centrifugal force against the machine part when it is stationary, so do not rotate.
  • the centrifugal elements are adjusted so far at the latest at an idle speed of the machine part due to the centrifugal force radially outward so far that the sealing lip rests with at least reduced force on the rotating machine part.
  • the centrifugal force elements and the spring force acting radially on them can be designed so that the sealing lip rests against the rotating machine part with only a minimal bearing force.
  • the radial forces can be ⁇ 5N.
  • the sealing lip can be made without overlap to the shaft. Then, the bearing force of the sealing lip on the shaft by the mass of the centrifugal elements and the radial force acting on them, preferably determined by the annular spring.
  • the sealing lip can also be made with a very small overlap to the shaft. Then the sealing lip is under low own radial force on the shaft.
  • the contact force is determined in this case by the centrifugal force segments, by the radial force acting on them, preferably by the annular spring, and the generated by the elastic deformation of the sealing lip own radial force.
  • the sealing lip at least from idle speed rotating machine part to form a small gap distance from the machine part is advantageous. Then takes place at rotating machine part no contact between the sealing lip and the machine part instead. The gap is at most so wide that a reliable recovery of the medium is ensured, which passes under the sealing lip. This is effected by return elements in the sealing lip.
  • centrifugal force elements are already displaced radially outwards under the action of centrifugal force when the rotational speed of the machine part has reached about 50% of the idling speed.
  • FIG. 1 is a front view of a radial shaft seal according to the invention
  • FIG. 2 is a side view of the radial shaft seal according to the invention shown in FIG. 1,
  • FIG. 3 is a perspective view of the radial shaft seal according to FIG. 1, FIG.
  • FIG. 6 is a section along the line EE in Figure 1 with a stationary shaft. to 12 in representations corresponding to FIGS. 1 to 6, the radial shaft seal according to the invention with rotating shaft.
  • the radial shaft seal described below is characterized in that its sealing lip rests on the shaft to be sealed with full radial force on it and seals. As soon as the shaft is rotatably driven, the sealing lip lifts off the rotating shaft or lies on it with only little radial force. In this way, the power loss is minimized by friction losses. This also means that the sealing lip is only subject to low wear and the radial shaft seal has a long life.
  • the radial shaft seal has an annular housing 1 which has an L-shaped cross section (FIG. 5). It has a cylindrical shell 2, to which a radially inwardly directed flange 3 connects. On its inside a sealing disc 4 is fixed with an annular fastening part 5.
  • the sealing disc 4 is advantageously a PTFE disc which is fixed in a known manner to the radial flange 3 of the housing 1.
  • the radially inner region of the sealing disc 4 is elastically bent in the installed position and forms a sealing lip 6, which rests sealingly on the shaft 7 to be sealed as a machine part, if it does not rotate or at a low speed.
  • a support ring 8 On the shaft 7 is rotatably a support ring 8, which has a Z-shaped cross-section and extends coaxially to the axis of the radial shaft seal.
  • the support ring 8 has a radially inner ring 9 which is fixed on the jacket of the shaft 7.
  • At the one axial end of the ring 9 includes a radially outwardly extending annular disc part 10, which connects the inner ring 9 with a radially outer ring 1 1. From the annular disc part 10, the two rings 9 and 1 1 extend in opposite axial directions.
  • the radially outer ring 1 1 is directed against the radial flange of the housing 1 and has a radial distance from the inner wall of the housing shell.
  • the radially outer cylindrical ring 1 1 of the support ring 8 surrounds a retaining ring 12, are secured axially with the centrifugal elements 13 and extending coaxially to the axis of the radial shaft seal.
  • the centrifugal elements 13 have rectangular cross-section and are formed part-ring-shaped.
  • the partial ring shape results from Fig. 1, in which the segments 13 are shown by dashed lines.
  • the segments 13 lie with their two flat side surfaces 14, 15 (Fig. 5) on the mutually facing inner sides of the locking ring 12 and the support ring 8 flat.
  • the centrifugal segments 13 are preferably made of higher density materials such as metallic materials or plastics with higher density fillers, e.g. Metal powder.
  • the specified materials are not intended to be limiting.
  • the cross-sectionally L-shaped locking ring 12 is located with a cylindrical ring member 16 on the inside of the cylindrical ring 1 1 of the support ring 8 at.
  • the front side of the ring member 16 is also located on the washer part 10 of the support ring 8.
  • To the ring member 16 of the locking ring 12 includes a radially inwardly extending flange 17, which extends parallel to the annular disc part 10 of the support ring 8 and ends approximately at the level of the radially inner ring 9 of the support ring 8.
  • the centrifugal elements 13 abut against the inside of the flange 17 of the retaining ring 12 and on the inside of the annular disc part 10 of the support ring 8.
  • the centrifugal elements 13 are provided in half circumferential length with a pin 18 which protrudes perpendicularly over the side surface 15 of the centrifugal elements 13 and protrudes through a slot 19 in the support ring 8 to the outside.
  • the slots 19 extend in the radial direction of the annular disc part 10 of the support ring 8 and extend to the radially inner ring 9 of the support ring 8.
  • the circumferential width of the slots 19 corresponds to the thickness or the diameter of the pins 18.
  • the radial shaft seal is provided with six annular centrifugal force elements 13, each having the pin 18 in half the circumferential length. Depending on the length of the centrifugal force elements 13, these may also have, for example, two spaced-apart pins, which engage in corresponding slots 19 of the carrier ring 8.
  • the pins 8 may also be connected to the carrier ring 8 and the slots 19 may be provided in the centrifugal elements 13.
  • the carrier ring 8 is exemplified as a transmitter wheel, which is part of a rotary encoder, with which the rotational position or position of the shaft 7 can be determined.
  • the support ring 8 is located on the air side of the radial shaft seal.
  • the sealing lip 6 extends from the radial flange 3 of the housing 1 in the direction of the air side. It is located in Fig. 5 right of the carrier ring. 8
  • the carrier ring 8 can also be designed without a rotary encoder function.
  • the area located to the right of the carrier ring 8 in FIG. 5 is the medium side. Then the centrifugal force is lubricated by the medium.
  • the sealing disc is bent in this case in the direction of the medium side, so that then the centrifugal force is on the medium side.
  • the centrifugal force elements 13 are force-loaded radially inwards so that they assume their radially inner position shown in FIGS. 1 to 6 at standstill of the shaft 7.
  • the force is applied by an annular spring 20 which is inserted in grooves 21 of the centrifugal force elements 13.
  • the grooves 21 are provided in the embodiment of the flange 17 of the retaining ring 12 facing side surface 14 of the centrifugal elements 13.
  • the grooves 21 may basically be provided in the opposite side surface 15 of the centrifugal elements 13.
  • the annular spring 20 extends over the circumference of all centrifugal elements 13 and loads them radially inwardly.
  • the annular spring 20 is secured by the retaining ring 12 against falling out of the grooves 21.
  • the grooves 21 are so deep that the annular spring 20 does not protrude from the grooves 21.
  • the grooves 21 and thus the annular spring 20 are provided so that they surround the pins 18 at a radial distance.
  • the pins 18 themselves lie on an imaginary circle about the axis of the radial shaft seal and each extend axially.
  • the pins 18 are suitably fixed in the centrifugal elements 13.
  • the support ring 8 and the retaining ring 12 are so composed that the end face 22 of the radially outer ring 1 1 of the support ring 8 and the housing flange facing the outside of the flange 17 of the retaining ring 12 are in a common radial plane of the radial shaft seal. Since the ring member 16 of the retaining ring 12 rests against the inner wall of the outer ring 1 1 of the support ring 8, no gap is formed at the transition from the ring 1 1 to the ring member 16, in which dirt particles and the like could set.
  • the flange 17 of the retaining ring 12 has sufficient distance from the fastening part 5 of the sealing disc 4, so that their function is not impaired.
  • the support ring 8 projects with its outer ring 1 1 partially
  • the annular disc part 10 of the carrier ring 8 lies completely outside the housing 1.
  • the centrifugal force elements 13 are arranged so that they rest in their radially inner position (FIGS. 1 to 6) on the free end of the sealing lip 6 and radially load them against the jacket of the shaft 7.
  • each centrifugal element 13 On the inner circumferential surface 24 of the centrifugal elements 13 at least one recess 25 is provided, which receives a lubricant.
  • the recess 25 may extend over the entire circumferential length of the respective centrifugal force element 13 or only over part of this circumferential length.
  • each centrifugal element 13 is provided with three recesses 25, each containing lubricant. It serves to minimize the friction between the respective centrifugal force element 13 and the sealing lip 6 when the shaft 7 is rotated starting from the standstill position.
  • the radial flange 17 of the retaining ring 12 has sufficient radial distance from the sealing disc 4 and its sealing lip 6, so that the sealing function is not affected by the retaining ring 12.
  • Figs. 1 to 6 the position of the centrifugal elements 13 is shown when the shaft 7 is not rotating. Then the centrifugal elements 13 are loaded by the annular spring 20 radially inwardly, so that they press the sealing lip 6 against the shell of the shaft 7 radially, so that when the shaft 7 a perfect seal is ensured. As a result, a standstill leakage is avoided when the shaft 7 is stationary.
  • the pins 18 are provided on the centrifugal force elements 13 in such a way that they still have a distance from the radially inner ring 9 of the carrier ring 8 in this position of the centrifugal force elements 13.
  • the centrifugal elements 13 are taken in the direction of rotation. By acting on the centrifugal force centrifugal force they are moved against the force of the annular spring 20 to the outside (Fig. 7 to 12), so that the sealing lip 6 can relax and also lifts from the shaft 7.
  • the maximum displacement of the centrifugal elements 13 is determined by the fact that they come to rest on the radially outer ring member 16 of the retaining ring 12 or the pins 18 on the radially outer slot 19 in the support ring 8. It is advantageous if the radial displacement of the centrifugal force elements 13 is limited by the fact that they come to rest on the ring member 16 of the locking ring 12. The pins 18 are thereby spared.
  • the sealing lip 6 can reliably stand out from the shaft 7.
  • the annular spring 20 is designed so that its force acting on the centrifugal force elements 13 radial force is less than that occurring during rotation of the shaft 7 and acting on the centrifugal elements 13 centrifugal force.
  • the bias of the annular spring 20 and the mass of the centrifugal elements 13 can be coordinated depending on the particular design of the radial shaft seal so that the centrifugal elements 13 are moved radially outward.
  • the radial shaft seal is formed so that the centrifugal force elements 13 are already displaced radially on reaching about 50% of the idle speed of the shaft by the centrifugal forces and the sealing lip 6 can lift off from the shaft 7 at this speed.
  • the power loss due to friction is thereby limited to a minimum. In a motor vehicle, this leads to a significant reduction in CO 2 - Emissions.
  • the wear of the sealing lip can be minimized because it is only in contact with the shaft 7 when it is at a standstill or has a speed that is less than about 50% of the idle speed of this shaft 7.
  • the sealing lip 6 is only at standstill or at this low speed on the shaft 7 and reliably prevents a standstill leakage.
  • the sealing lip 6 may be provided on its underside facing the shaft 7 with a (not shown) return conveyor structure, with which the dynamic tightness can be realized, in particular, even if the sealing lip 6 is lifted from the shaft 7.
  • the sealing lip 6 can lift off at the corresponding speed of the shaft 7, the sealing lip 6 is advantageously designed without overlap to the shaft 7. It is a defined gap 26 (Fig. 1 1) admitted to the shaft 7. Thus, despite this gap 26 between the sealing lip 6 and the shaft 7, a dynamic seal is achieved, the sealing lip 6 is formed so that it extends over a larger axial area coaxial with the jacket of the shaft 7 and on its shaft 7 facing bottom the Return conveyor structure, for example, a spiral spiral having. Such a design ensures a perfect dynamic seal despite the raised sealing lip 6.
  • the width of the gap 26 is only so great that the return conveyor structure for the recovery of the reaching under the sealing lip 6 medium can be effective. In practice, the maximum gap width is about 0.1 mm.
  • the radial shaft seal itself does not need to be rotated.
  • the Abhebezeittician the sealing lip 6 of the shaft 7 can be easily adjusted on the design of the annular spring 20 and the mass of the centrifugal elements 13. This centrifugal mechanics is not very sensitive to temperature, so that it can be used even at low temperatures.
  • the annular spring 20 can be the contact pressure the sealing lip 6 optimally tune to the particular application of the radial shaft seal.
  • centrifugal force mechanism described makes it possible to use even highly friction-reduced PTFE sealing disks, which have hitherto not been used due to poor air leakage values.
  • the centrifugal force with the support ring 8, the centrifugal segments 13 and the locking ring 12 is located on the atmosphere or air side of the radial shaft seal.
  • the radial shaft seal can also be used for internal combustion engines with an automatic start-stop system.
  • the engine is switched off when the vehicle is stationary, so that the shaft 7 is stationary.
  • the centrifugal force elements 13 the sealing lip 6 is pressed against the shaft 7 in the manner described, so that a reliable seal is ensured.
  • the abutment of the sealing lip 6 on the shaft 7 already takes place when the rotational speed of the shaft 7 is approximately below 50% of the idling speed. Since the carrier ring 8 is provided with the encoder wheel in the described advantageous embodiment, the rotational position and the direction of rotation of the shaft 7 can be determined perfectly in a start-stop system.
  • the sealing lip 6 lifts at a corresponding speed of the shaft 7, so that it has no contact with her.
  • the radial shaft seal can also be designed so that the sealing lip 6 does not lift off the shaft 7, but only rests against it under a very small force.
  • the annular spring 20 is designed so that the centrifugal force segments 13 only so far lift that the sealing lip 6 rests with minimal force on the jacket of the shaft 7.
  • the minimum bearing force for example, be less than 5N. Due to these very low radial forces, the advantage of friction reduction is maintained.
  • the sealing lip 6 can rest at the appropriate speed and lifted centrifugal force elements 13 but, for example, with very little own radial force on the shaft 7. In this case, the sealing lip 6 is made with very little overlap.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing With Elastic Sealing Lips (AREA)

Abstract

L'invention concerne un joint d'étanchéité d'arbre radial comportant un élément d'étanchéité qui est muni d'une lèvre d'étanchéité (6) appliquée, dans une position d'étanchéité, sur une pièce de machine (7) à rendre étanche, entraînée en rotation. L'invention vise à limiter les pertes de friction. À cet effet, la lèvre d'étanchéité (6) est entourée d'au moins deux éléments à force centrifuge (13) qui sont maintenus sur au moins un support (8) relié solidaire en rotation à la pièce de machine (7), et qui sollicitent la lèvre d'étanchéité (6) radialement dans la position d'étanchéité lorsque la pièce de machine (7) est à l'arrêt et ne la sollicitent pas lorsque la pièce de machine (7) tourne. L'invention concerne également un procédé permettant de rendre étanche une pièce tournante de machine (7) au moyen d'un joint d'étanchéité d'arbre radial, selon lequel la lèvre d'étanchéité (6) est comprimée contre la pièce de machine (7) par les éléments à force centrifuge (13) lorsque la pièce de machine (7) est à l'arrêt et, au plus tard lorsque la pièce de machine (7) est au ralenti, est déplacée suffisamment loin vers l'extérieur pour que la lèvre d'étanchéité (6) soit appliquée sur la pièce de machine (7) avec une force au moins réduite.
PCT/EP2016/002112 2015-12-17 2016-12-14 Joint d'étanchéité d'arbre radial et procédé permettant de rendre étanche une pièce tournante de machine au moyen d'un joint d'étanchéité d'arbre radial Ceased WO2017102081A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201680080233.4A CN108700197A (zh) 2015-12-17 2016-12-14 径向轴密封系统以及用于利用径向轴密封系统密封转动式机械部件的方法

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015016642.5A DE102015016642B4 (de) 2015-12-17 2015-12-17 Radialwellendichtung sowie Verfahren zum Abdichten eines drehenden Maschinenteils mit einer Radialwellendichtung
DE102015016642.5 2015-12-17

Publications (1)

Publication Number Publication Date
WO2017102081A1 true WO2017102081A1 (fr) 2017-06-22

Family

ID=57749884

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PCT/EP2016/002112 Ceased WO2017102081A1 (fr) 2015-12-17 2016-12-14 Joint d'étanchéité d'arbre radial et procédé permettant de rendre étanche une pièce tournante de machine au moyen d'un joint d'étanchéité d'arbre radial

Country Status (3)

Country Link
CN (1) CN108700197A (fr)
DE (1) DE102015016642B4 (fr)
WO (1) WO2017102081A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017011541A1 (de) * 2017-12-08 2019-06-13 Kaco Gmbh + Co. Kg Dichtung, insbesondere Radialwellendichtung, und Verfahren zum Abdichten, insbesondere unter Verwendung einer solchen Dichtung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1003653A (fr) * 1947-02-06 1952-03-20 Dispositif d'étanchéité, en particulier pour embrayages ou accouplements hydrauliques
DE19600125A1 (de) * 1996-01-04 1997-07-10 Fag Oem & Handel Ag Dichtung mit fliehkraftentlasteter Dichtlippe
EP2497977A1 (fr) * 2011-03-09 2012-09-12 Lenze Drives GmbH Dispositif de joint pour arbre
DE102012107382A1 (de) * 2012-08-10 2014-02-13 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Radialwellendichtring

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GB182441A (en) * 1921-06-28 1922-11-30 Escher Wyss Maschf Ag Improvements in packing box packings for rotary compressors used in refrigerating and other plants
US3256027A (en) * 1965-05-14 1966-06-14 Univ Oklahoma State Fluid seal
DE2248274A1 (de) * 1972-10-02 1974-04-18 Allg Ind Commerz Walter Von We Einrichtung zur erzeugung einer reihe von elektrischen impulsen, deren haeufigkeit der drehzahl eines kraftfahrzeugrades proportional ist
CN1039475A (zh) * 1988-07-16 1990-02-07 成都科技大学 外装型动力式自紧停车密封
EP1488144B1 (fr) * 2002-03-26 2010-11-24 Federal-Mogul Corporation Element d'etancheite pour arbre
ITTO20040340A1 (it) * 2004-05-21 2004-08-21 Skf Ab Dispositivo di tenuta per un cuscinetto di rotolamento
US8403333B2 (en) * 2010-09-17 2013-03-26 Freudenberg-Nok General Partnership Zero torque membrane seal
CN201844020U (zh) * 2010-09-21 2011-05-25 青岛开世密封工业有限公司 带有切口式回流线的ptfe片

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1003653A (fr) * 1947-02-06 1952-03-20 Dispositif d'étanchéité, en particulier pour embrayages ou accouplements hydrauliques
DE19600125A1 (de) * 1996-01-04 1997-07-10 Fag Oem & Handel Ag Dichtung mit fliehkraftentlasteter Dichtlippe
EP2497977A1 (fr) * 2011-03-09 2012-09-12 Lenze Drives GmbH Dispositif de joint pour arbre
DE102012107382A1 (de) * 2012-08-10 2014-02-13 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Radialwellendichtring

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Publication number Publication date
DE102015016642A1 (de) 2017-06-22
DE102015016642B4 (de) 2019-03-14
CN108700197A (zh) 2018-10-23

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