WO2024088461A1 - Rolling bearing - Google Patents

Rolling bearing Download PDF

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Publication number
WO2024088461A1
WO2024088461A1 PCT/DE2023/100681 DE2023100681W WO2024088461A1 WO 2024088461 A1 WO2024088461 A1 WO 2024088461A1 DE 2023100681 W DE2023100681 W DE 2023100681W WO 2024088461 A1 WO2024088461 A1 WO 2024088461A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
rolling
ring
section
inner ring
Prior art date
Application number
PCT/DE2023/100681
Other languages
German (de)
French (fr)
Inventor
Beate Schmidt
Claus Guckenberger
Sebastian Meyer
Original Assignee
Schaeffler Technologies AG & 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 Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2024088461A1 publication Critical patent/WO2024088461A1/en

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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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7886—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted outside the gap between the inner and outer races, e.g. sealing rings mounted to an end face or outer surface of a race
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward
    • F16C33/7879—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a further sealing ring
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/80—Labyrinth sealings
    • F16C33/805—Labyrinth sealings in addition to other sealings, e.g. dirt guards to protect sealings with sealing lips
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/20—Application independent of particular apparatuses related to type of movement
    • F16C2300/22—High-speed rotation
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
    • F16C33/7853—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with one or more sealing lips to contact the inner race
    • F16C33/7856—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with one or more sealing lips to contact the inner race with a single sealing lip

Definitions

  • the invention relates to a rolling bearing with a cover plate and a seal.
  • DE 10 2018 123 495 A1 discloses a ball bearing with a rotating bearing inner ring and a torsionally rigid bearing outer ring, which has a sealing arrangement on both sides.
  • the sealing arrangement consists of a one-piece centrifugal disk made of steel, which is fixed in position on the bearing inner ring by force. A sealing collar of the centrifugal disk is guided contactlessly to a sealing surface of the bearing outer ring while maintaining a gap dimension.
  • WO 2010/054890 A1 discloses a sealing arrangement with a sealing ring and a slinger ring, which has a cylindrical fastening part.
  • the sealing ring has a radial, pre-stressed sealing lip, which makes contact with the cylindrical fastening part of the slinger ring. Defined distances and component design are intended to prevent the radial sealing lip from folding over in the direction of the rolling space.
  • the invention is based on the object of providing an improved rolling bearing.
  • this object is achieved by a rolling bearing with a bearing outer ring arranged about an axis of rotation running in the axial direction, which has a first raceway, and a bearing inner ring arranged concentrically thereto, which has a second raceway opposite the first raceway in the radial direction, with a cage which rotatably guides rolling elements rolling on the raceways in a row of rolling elements, and with a cover disk and a seal, both of which are arranged radially between the bearing inner ring and the bearing outer ring, wherein the cover disk is attached to the bearing inner ring and the sealing ring is arranged axially between the row of rolling elements and the cover disk and has a sealing lip which makes contact with the bearing inner ring.
  • the rolling bearing is designed in particular as a ball bearing or as a flange bearing and is arranged around a rotation axis.
  • the rotation axis runs in the axial direction.
  • a radial direction runs perpendicular to the rotation axis.
  • a bearing outer ring, a bearing inner ring and a cage are arranged circumferentially around the rotation axis.
  • the cage can be made of metallic materials or as a plastic cage, in particular PA66-GF25, PA46-GF30.
  • the bearing outer ring and bearing inner ring are arranged in such a way that the bearing outer ring is radially further away from the rotation axis than the bearing inner ring.
  • rollers Between the bearing outer ring and the bearing inner ring, rollers roll on a first raceway on the bearing outer ring and a
  • the second raceway on the bearing inner ring has rolling elements in a row of rolling elements. These are designed in particular as ball rolling elements, but can also be designed as cylindrical rollers, tapered rollers or needle rollers.
  • the invention is based on the knowledge that it is expedient to use a combination of a friction-optimized seal and a cover plate that acts as a centrifugal disk to efficiently seal the interior of the rolling bearing at high speeds.
  • the cover plate is arranged on one or both axial ends of the rolling bearing between the bearing inner ring and the bearing outer ring, i.e. on one or both sides of the rolling bearing with a relatively large distance to the row of rolling elements.
  • the cover plate is adjacent to the bearing inner ring in the radial direction.
  • the cover plate can be firmly connected to the bearing inner ring in a force-fitting or form-fitting manner or also after force and form-fitting.
  • the cover plate largely covers a radial gap that is formed between the bearing inner ring and the bearing outer ring in the radial direction.
  • the cover plate forms a gap seal with a radial inner rim of the bearing outer ring, i.e. the rim on the bearing outer ring, which also has the first raceway in its axial extension.
  • the cover plate is combined with a sealing ring.
  • the sealing ring is arranged in the axial direction between the cover plate and the row of rolling elements and therefore does not require any additional installation space.
  • the sealing ring runs radially and bridges the radial gap between the bearing outer ring and the bearing inner ring.
  • the sealing ring consists of a solid part, such as a reinforcement, which is partially or completely enclosed by an elastomer part.
  • the sealing ring has a sealing body and a fastening bead in the radial direction, with which it is arranged on the bearing outer ring.
  • the sealing body On the radially opposite side, the sealing body has a sealing lip which is tangent to the bearing inner ring.
  • the bearing inner ring is the rotating bearing ring in the rolling bearing during operation
  • the fixed connection of the cover plate to the bearing inner ring means that it rotates with the bearing inner ring.
  • the bearing outer ring would be In this case, it is mounted in a rotationally rigid manner.
  • the rotation of the cover plate means that the rolling bearing can be largely shielded from surrounding media.
  • the cover plate uses centrifugal force to throw incoming media and disruptive particles away from the rolling bearing, thus acting as a centrifugal disc. It keeps most incoming media away.
  • the seal which has a sealing lip on the bearing inner ring, acts as a further means of shielding the interior of the rolling bearing.
  • the radially aligned sealing lip does not make contact with a section of the cover plate, but rather touches the bearing inner ring directly.
  • the seal is designed as a friction-optimized seal and has a surface on its sealing lip with a low coefficient of friction or properties that reduce the friction between the sealing lip and the bearing inner ring.
  • the combination of the sealing ring with the friction-optimized sealing lip on the bearing inner ring and the cover plate arranged on the bearing inner ring means that lubricating media can be kept in the rolling bearing and at the same time disruptive particles can be efficiently prevented from entering the rolling bearing.
  • the interior of the bearing is efficiently sealed at high speeds and does not require any costly components or additional space in the rolling bearing environment.
  • the cover plate preferably has recesses.
  • the recesses are arranged adjacent to one another in a continuous manner.
  • the recesses are preferably arranged on an end section of the cover plate facing the bearing inner ring.
  • the recesses can be in the form of holes which are circular, oval or have an elongated hole shape.
  • the recesses can also be slots with different extensions in their course.
  • the slots can be straight or curved in their basic form or consist of a combination of different geometries.
  • the recesses are distributed in the circumferential direction over the cover plate and thus adjacent to one another.
  • the recesses can be arranged evenly or in a chaotic pattern or in a further distribution which is advantageous for an application along the cover plate.
  • the recesses are preferably located on a section of the cover plate.
  • cover plate which is located in the third of the total radial length of the cover plate that is closest to the bearing inner ring. Starting from the bearing outer ring, this is the end section of the cover plate.
  • the recesses allow the rolling bearing to be drained during operation and, if the recesses are arranged all around, also when the rolling bearing is at rest. This prevents stagnant media and reliably prevents reactions between media and the seal caused by this.
  • the sealing ring preferably has a further sealing lip which makes contact with the cover plate.
  • the further sealing lip is aligned at an angle to the cover plate.
  • the sealing ring preferably has a further sealing lip which rests on the cover plate.
  • the further sealing lip runs at an angle to the cover plate.
  • Two chambers are formed by the further sealing lip. A gap between the cover plate and a radial inner edge of the bearing outer ring, which is radially opposite the cover plate, forms the entrance to the first chamber.
  • the first chamber is delimited by the further sealing lip.
  • the second chamber is located between the further sealing lip, the sealing lip and part of the cover plate and has no opening.
  • Particles which pass through the rotating cover plate in its function as a centrifugal disk first reach the first chamber, with the further sealing lip forming a barrier. If the additional sealing lip is also inclined towards the cover plate with a tendency to tilt towards the bearing outer ring, disruptive particles collect in a groove between the additional sealing lip and the sealing body. The centrifugal force causes the particles to be thrown back towards the bearing outer ring during operation. If particles do manage to overcome the additional sealing lip, they are still not inside the rolling bearing, but only in the second chamber, where the sealing lip prevents them from penetrating into the rolling bearing interior.
  • the additional sealing lip has a surface with a low coefficient of friction or properties that reduce the friction between the other sealing lip and the cover plate.
  • This design of the rolling bearing therefore makes use of high speeds for the functionality of one of the two components of the seal, namely the cover plate.
  • a seal with a friction-optimized sealing lip that rests on the bearing inner ring and another friction-optimized sealing lip that rests on the cover plate a reliable seal of the rolling bearing interior can be achieved with high energy efficiency and little installation space.
  • the cover disk preferably has a section that runs diagonally towards the row of rolling elements.
  • the cover disk preferably has a section that runs neither purely in the axial direction nor purely in the radial direction, but rather diagonally towards the row of rolling elements.
  • the middle section comprises at least the third of the cover disk that also contains the center of the cover disk in the radial direction.
  • a section is therefore said to run diagonally towards the row of rolling elements if it has a smaller axial distance to a straight line running radially through the center of the rolling elements than the radially running middle section.
  • the section that runs diagonally towards the row of rolling elements forms a guide surface on the cover disk. The aim of this is to guide media that have overcome the cover plate and, promoted by the centrifugal force acting during operation, to allow them to escape again in a controlled manner.
  • the cover plate has a section running parallel to a radial inner rim of the bearing outer ring and a C-shaped section.
  • the cover plate disc has a section which is arranged on the bearing outer ring and runs axially.
  • the bearing outer ring has a boundary surface on its radially inner side, i.e. on the side facing the rolling elements, a radial inner rim.
  • a section of the cover disc runs parallel to this radial inner rim at one axial end of the bearing outer ring, with a gap seal being formed between the radial inner rim of the bearing outer ring and the cover disc.
  • the cover disc also has a C-shaped section. The opening of the C can be oriented towards the row of rolling elements, away from the row of rolling elements or towards the bearing outer ring or the bearing inner ring.
  • the bearing outer ring and/or the bearing inner ring have a current-insulating layer.
  • the bearing outer ring or the bearing inner ring or the bearing inner ring and the bearing inner ring have a layer that does not conduct electricity. This prevents current from flowing through the rolling bearing, which can increase the service life of the rolling bearing.
  • the cover disk on the bearing inner ring has a C-shaped section with adjacent recesses all the way around, the C-shaped section being followed by a section which, starting from a radially running central section, runs diagonally towards the row of rolling elements, this section running diagonally towards the row of rolling elements being followed by the radially running central section, which is followed by a section running diagonally towards the row of rolling elements, and the cover disk in the area of the bearing outer ring having a section running parallel to a radial inner rim of the bearing outer ring.
  • the cover disk is divided into different sections. In a central section, the cover disk runs in a radial direction and runs in a straight line.
  • the cover disk has a section on each side radially which runs diagonally and is oriented in the direction of the row of rolling elements.
  • the diagonally running sections therefore run diagonally from the central section away and towards the row of rolling elements, thereby reducing the axial distance to the row of rolling elements.
  • In the direction of the inner bearing ring there is a section in the shape of a C, which rests against a rim of the inner bearing ring oriented towards the outer ring.
  • the section running diagonally towards the row of rolling elements is followed by another section, which ends in a section running parallel to a radial inner rim of the outer bearing ring. A gap seal is thus formed between the radial inner rim of the outer bearing ring and the cover plate.
  • Figure 1 is a schematic diagram of the rolling bearing according to the invention in a perspective view
  • Figure 2 shows a schematic diagram of an embodiment of the rolling bearing according to the invention in a sectional partial view
  • Figure 3 is a schematic diagram of another embodiment of the rolling bearing according to the invention in a partial sectional view.
  • Figure 1 shows a perspective view of a rolling bearing 1 according to the invention designed as a ball bearing.
  • the direction of the rotation axis 2 is in the direction of the rotation axis 2.
  • the direction of the rotation axis 2 is perpendicular to the rotation axis 2.
  • the rolling bearing 1 is composed of a bearing inner ring 5 arranged around a rotation axis 2 and a bearing outer ring 3 of larger diameter arranged concentrically thereto.
  • a gap i.e. a radial gap, is formed between the bearing outer ring 3 and the bearing inner ring 5 in the radial direction r.
  • This radial gap is formed by a cover disk 10, which is circumferential and extends in the radial direction r from the bearing inner ring 5 to the bearing outer ring 3.
  • the cover disk 10 is not flat in the radial direction r, but has elevations and depressions and is thus divided into different sections.
  • Adjacent to the bearing inner ring 5, the cover disk 10 has an end section 15.
  • the end section 15 has recesses 14 that are evenly distributed all around and are designed in the shape of a part circle. The recesses 14 enable drainage of the rolling bearing 1 both during operation and when at rest.
  • FIG. 2 shows a sectional partial view of an embodiment of the rolling bearing 1 according to the invention.
  • the rolling bearing 1 is designed as a ball bearing with a bearing inner ring 5 arranged around a rotation axis 2 and a bearing outer ring 3 arranged concentrically thereto, between which a radial gap is formed in the radial direction r, i.e. perpendicular to the rotation axis 2.
  • the bearing outer ring 3 has a first raceway 4 for rolling elements 8.
  • the bearing inner ring 5 opposite it in the radial direction r has a second raceway 6 for rolling elements 8.
  • a cage 7 guides the rolling elements 8 so that they can rotate on the raceways 4, 6 in a row of rolling elements 9.
  • the bearing outer ring 3 has a radial inner rim 12 on the bearing outer ring 3. This runs in the axial direction a, i.e. along the rotation axis 2, and abruptly reduces its radial extent.
  • the radial inner rim 12 forms a first groove 21 and then continues to an axial end of the rolling bearing 1.
  • a radial inner rim 23 of the bearing inner ring 5 is located opposite the radial inner rim 12 of the bearing outer ring 3 in the radial direction r. This runs in the axial direction a and abruptly reduces its radial extent.
  • the radial inner rim 23 forms a second groove 22 and then continues to an axial end of the rolling bearing 1.
  • a sealing ring 11 is arranged on the first groove 21 directly adjacent to the row of rolling elements 9 and extends radially to the bearing inner ring 5.
  • the sealing ring 11 has a sealing lip 13 which contacts the radial inner rim 23 of the bearing inner ring 5.
  • a cover disk 10 is arranged on the second groove 22 adjacent to the sealing ring 11 in the axial direction a. This bridges the gap between the bearing inner ring 5 and the bearing outer ring. ring 3, whereby a gap remains between the cover disk 10 and the radial inner rim 12 of the bearing outer ring 3.
  • the cover disk 10 has recesses 14.
  • the recesses 14 implement drainage of the rolling bearing 1 both when stationary and during operation.
  • the cover disk 10 is made up of various sections 17, 18, 19, 20.
  • the cover disk 10 On the bearing inner ring 5, the cover disk 10 has a C-shaped section 20, in the middle area a radial middle section 19, which runs in the radial direction r. Starting from the radial middle section 19, a section 17 adjoins both sides, which runs at an angle to the row of rolling elements 9.
  • the cover disk 10 On the radial inner rim 12 of the bearing outer ring 3, the cover disk 10 has a section 18 which runs parallel to the radial inner rim 12.
  • the bearing inner ring 5 rotates with the cover plate 10 arranged there.
  • the sealing ring 11 remains static, as does the bearing outer ring 3.
  • Media and contaminants flowing in axially on the side of the cover plate 10 bounce off the cover plate 10 or are thrown away from the cover plate 10 by centrifugal force.
  • Media and disruptive particles that get past the cover plate 10 are prevented from entering the interior of the rolling bearing 1 by the sealing ring 11 integrated into the rolling bearing 1.
  • media such as condensation water that forms during operation can escape through the recesses 14 on the cover plate 10. This prevents stagnant media on the sealing ring 11, which would damage the sealing ring 11 and thus cause it to fail prematurely.
  • FIG. 3 shows a further embodiment of a rolling bearing 1 according to the invention in a sectional partial view.
  • the rolling bearing 1 is arranged analogously to the rolling bearing 1 from Figure 2 around a rotation axis 2 running in the axial direction a and has a bearing outer ring 3 with a first raceway 4, a bearing inner ring 5 with a second raceway 6, rolling elements 8 in a row of rolling elements 9, guided by a cage 7.
  • a radial direction r is aligned perpendicular to the rotation axis 2.
  • a radial inner rim 12 of the bearing outer ring 3 is designed analogously to Figure 2 and has a first groove 21.
  • the bearing inner ring 5 has a radial inner rim 23 with a second groove 22.
  • a sealing ring 11 is arranged on the first groove 21, and a cover disk 10 on the second groove 22.
  • the sealing ring 11 has a further sealing lip 16 in addition to a sealing lip 13 which rubs against the bearing inner ring 5, but no openings for drainage.
  • the further sealing lip 16 originates from the sealing ring 11, runs inclined to the rotation axis 2 at an angle to the cover disk 10 and contacts the cover disk 10 on the side facing the row of rolling elements 9.
  • the cover disk 10 is arranged on the bearing inner ring 5 in a similar way to Figure 2 and is divided into several sections 17, 18, 19, 20. It has a section 18 running parallel to the radial inner rim 12 of the bearing outer ring 3, a middle radial section 19, a C-shaped section 20 and sections 17 which run at an angle to the row of rolling elements 9.
  • the additional sealing lip 16 creates an additional hurdle to prevent surrounding media from entering the interior of the rolling bearing 1.
  • Media which are located inside the rolling bearing 1 and are intended to remain there, such as lubricating media, are held inside by the additional sealing lip 16.
  • any medium which hits it is thrown away by the cover disk 10 which rotates together with the bearing inner ring 5.
  • Particles which nevertheless penetrate through the remaining gap between the cover disk 10 and the radial inner rim 12 of the bearing outer ring 3 are intercepted by the additional sealing lip 16 on the sealing ring 11. If media pass through the additional sealing lip 16 during operation, the sealing lip 13 remains as an additional instance to prevent these media from entering the interior of the rolling bearing 1. This increases the sealing efficiency further increased and the interior of the rolling bearing 1 is reliably sealed even at high speeds.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

The invention relates to a rolling bearing (1) which is arranged about a rotational axis (2) that runs in the axial direction a, comprising an outer bearing ring (3) with a radial inner edge (12), an inner bearing ring (5), a cage (7), raceways (4, 6) on which rolling bodies (8) in a rolling body row (9) roll, a seal ring (11) which runs in the radial direction r and has a seal lip (13), and a radially running cover disc (10) which is arranged on the inner bearing ring (5) and which functions as a centrifugal disc and is divided into differently running sections (17, 18, 19, 20), wherein according to the embodiment, an end section (15) can have recesses (14).

Description

Bezeichnung der Erfindung Description of the invention
Wälzlager Roller bearing
Gebiet der Erfindung Field of the invention
Die Erfindung betrifft ein Wälzlager mit einer Abdeckscheibe und einer Dichtung. The invention relates to a rolling bearing with a cover plate and a seal.
Hintergrund der Erfindung Background of the invention
DE 10 2018 123 495 A1 offenbart ein Kugellager mit einem rotierenden Lagerinnenring und einem drehstarren Lageraußenring, welches auf beiden Seiten eine Dichtungsanordnung aufweist. Die Dichtungsanordnung besteht aus einer einteiligen, aus Stahl hergestellten Schleuderscheibe, die kraftschlüssig am Lagerinnenrings lagefixiert ist. Dabei ist ein Dichtkragen der Schleuderscheibe berührungslos unter Einhaltung eines Spaltmaßes bis an eine Dichtfläche des Lageraußenrings geführt. DE 10 2018 123 495 A1 discloses a ball bearing with a rotating bearing inner ring and a torsionally rigid bearing outer ring, which has a sealing arrangement on both sides. The sealing arrangement consists of a one-piece centrifugal disk made of steel, which is fixed in position on the bearing inner ring by force. A sealing collar of the centrifugal disk is guided contactlessly to a sealing surface of the bearing outer ring while maintaining a gap dimension.
WO 2010/054890 A1 offenbart eine Dichtungsanordnung mit einem Dichtungsring und einem Schleuderring, welcher ein zylindrisches Befestigungsteil aufweist. Der Dichtring weist eine radiale, vorspannungsverstärkte Dichtlippe auf, welche mit dem zylindrischen Befestigungsteil des Schleuderrings Kontakt macht. Durch definierte Abstände und Komponentenauslegung soll vermieden werden, dass die radiale Dichtlippe in Richtung des Wälzraumes umklappen kann. WO 2010/054890 A1 discloses a sealing arrangement with a sealing ring and a slinger ring, which has a cylindrical fastening part. The sealing ring has a radial, pre-stressed sealing lip, which makes contact with the cylindrical fastening part of the slinger ring. Defined distances and component design are intended to prevent the radial sealing lip from folding over in the direction of the rolling space.
Liegen hohe Dichtungsanforderung vor, kommen je nach Anwendung zusätzlich externe Dichtungen zum Einsatz, welche dem Wälzlager vorgeschaltet werden wie in US2022003319AA oder US 2021/0348646 A1. Diese benötigen jedoch mehr Bauraum und verursachen, bedingt durch ihre Bauart eine höhere Reibung. Je größer die Drehzahl wird, desto höher wird die Wärmeentwicklung im Wälzlager, was eine Anpassung der Kühlleistung erfordert und unter anderem zu einer Reduzierung der Energieeffizienz führt. Zudem wird der Montageaufwand durch zusätzliche Komponenten erhöht und damit die Wirtschaftlichkeit des Wälzlagers herabgesetzt. If there are high sealing requirements, depending on the application, additional external seals are used, which are installed upstream of the rolling bearing as in US2022003319AA or US 2021/0348646 A1. However, these require more installation space and, due to their design, cause higher friction. The higher the speed, the higher the heat development in the rolling bearing, which requires an adjustment of the cooling capacity and, among other things, leads to a reduction in energy efficiency. In addition, the assembly effort is increased by additional components and thus the economic efficiency of the rolling bearing is reduced.
Aufgabe der Erfindung Object of the invention
Der Erfindung liegt die Aufgabe zugrunde, ein verbessertes Wälzlager anzugeben. The invention is based on the object of providing an improved rolling bearing.
Beschreibung der Erfindung Description of the invention
Erfindungsgemäß wird diese Aufgabe gelöst durch ein Wälzlager mit einem um eine in axiale Richtung verlaufende Rotationsachse angeordneten Lageraußenring, welcher eine erste Laufbahn aufweist, und einem konzentrisch dazu angeordneten Lagerinnenring, welcher eine, der ersten Laufbahn in radiale Richtung gegenüberliegende zweite Laufbahn aufweist, mit einem Käfig welcher auf den Laufbahnen abrollende Wälzkörper in einer Wälzkörperreihe drehbar führt, sowie einer Abdeckscheibe und einem Dichtung, welche beide radial zwischen dem Lagerinnenring und dem Lageraußenring angeordnet sind, wobei die Abdeckscheibe am Lagerinnenring angebracht ist und der Dichtring axial zwischen der Wälzkörperreihe und der Abdeckscheibe angeordnet ist und eine Dichtlippe aufweist, welche mit dem Lagerinnenring Kontakt macht. According to the invention, this object is achieved by a rolling bearing with a bearing outer ring arranged about an axis of rotation running in the axial direction, which has a first raceway, and a bearing inner ring arranged concentrically thereto, which has a second raceway opposite the first raceway in the radial direction, with a cage which rotatably guides rolling elements rolling on the raceways in a row of rolling elements, and with a cover disk and a seal, both of which are arranged radially between the bearing inner ring and the bearing outer ring, wherein the cover disk is attached to the bearing inner ring and the sealing ring is arranged axially between the row of rolling elements and the cover disk and has a sealing lip which makes contact with the bearing inner ring.
Das Wälzlager ist insbesondere als Kugellager oder auch als Flanschlager ausgebildet und ist um eine Rotationsachse angeordnet. Die Rotationsachse verläuft in axialer Richtung. Eine radiale Richtung verläuft senkrecht zur Rotationsachse. Ein Lageraußenring, ein Lagerinnenring und ein Käfig sind umlaufend um die Rotationsachse angeordnet. Dabei kann der Käfig aus metallischen Werkstoffen oder auch als Kunststoffkäfig, insbesondere aus PA66-GF25, PA46-GF30, ausgeführt sein. Lageraußenring und Lagerinnenring sind so angeordnet, dass der Lageraußenring radial weiter von der Rotationsachse beab- standet ist als der Lagerinnenring. Zwischen dem Lageraußenring und dem Lagerinnenring wälzen auf einer ersten Laufbahn am Lageraußenring und einer zweiten Laufbahn am Lagerinnenring Wälzkörper in einer Wälzkörperreihe ab. Diese sind insbesondere als Kugelwälzkörper ausgebildet, können jedoch auch als Zylinderrollen, Kegelrollen oder Nadelrollen ausgeführt sein. The rolling bearing is designed in particular as a ball bearing or as a flange bearing and is arranged around a rotation axis. The rotation axis runs in the axial direction. A radial direction runs perpendicular to the rotation axis. A bearing outer ring, a bearing inner ring and a cage are arranged circumferentially around the rotation axis. The cage can be made of metallic materials or as a plastic cage, in particular PA66-GF25, PA46-GF30. The bearing outer ring and bearing inner ring are arranged in such a way that the bearing outer ring is radially further away from the rotation axis than the bearing inner ring. Between the bearing outer ring and the bearing inner ring, rollers roll on a first raceway on the bearing outer ring and a The second raceway on the bearing inner ring has rolling elements in a row of rolling elements. These are designed in particular as ball rolling elements, but can also be designed as cylindrical rollers, tapered rollers or needle rollers.
Der Erfindung liegt die Erkenntnis zugrunde, dass es zielführend ist zur effizienten Abdichtung des Inneren des Wälzlagers bei hohen Drehzahlen eine Kombination aus einer reibungsoptimierten Dichtung und einer als Schleuderscheibe fungierenden Abdeckscheibe heranzuziehen. Die Abdeckscheibe ist an einem oder beiden axialen Enden des Wälzlagers zwischen Lagerinnenring und Lageraußenring angeordnet, also auf einer oder beiden Seiten des Wälzlagers mit relativ großem Abstand zur Wälzkörperreihe. Zudem ist die Abdeckscheibe in radialer Richtung an den Lagerinnenring angrenzend. Die Abdeckscheibe kann dabei kraftschlüssig oder formschlüssig oder auch nach Kraft- und Formschluss fest mit dem Lagerinnenring verbunden sein. Die Abdeckscheibe deckt einen radialen Spalt, der zwischen Lagerinnenring und Lageraußenring in radialer Richtung gebildet ist, weitgehend ab. Die Abdeckscheibe bildet mit einem radialen Innenbord des Lageraußenrings, also dem Bord am Lageraußenring, welcher in seiner axialen Verlängerung auch die erste Laufbahn aufweist, eine Spaltdichtung. Um nun die Effizienz der Abdichtfunktion weiter zu steigern, wird die Abdeckscheibe mit einem Dichtring kombiniert. Dabei ist der Dichtring in axialer Richtung zwischen Abdeckscheibe und Wälzkörperreihe angeordnet und benötigt so keinen zusätzlichen Bauraum. Der Dichtring verläuft radial und überbrückt den Radialspalt zwischen Lageraußenring und Lagerinnenring. Der Dichtring besteht aus einem festen Anteil, wie einer Armierung, welcher teilweise oder gänzlich eingefasst ist von einem elastomeren Anteil. Der Dichtring weist einen Dichtkörper und in radialer Richtung eine Befestigungswulst auf, mit welcher er am Lageraußenring angeordnet ist. Auf der radial gegenüberliegenden Seite weist der Dichtkörper eine Dichtlippe auf, welche den Lagerinnenring tangiert. The invention is based on the knowledge that it is expedient to use a combination of a friction-optimized seal and a cover plate that acts as a centrifugal disk to efficiently seal the interior of the rolling bearing at high speeds. The cover plate is arranged on one or both axial ends of the rolling bearing between the bearing inner ring and the bearing outer ring, i.e. on one or both sides of the rolling bearing with a relatively large distance to the row of rolling elements. In addition, the cover plate is adjacent to the bearing inner ring in the radial direction. The cover plate can be firmly connected to the bearing inner ring in a force-fitting or form-fitting manner or also after force and form-fitting. The cover plate largely covers a radial gap that is formed between the bearing inner ring and the bearing outer ring in the radial direction. The cover plate forms a gap seal with a radial inner rim of the bearing outer ring, i.e. the rim on the bearing outer ring, which also has the first raceway in its axial extension. In order to further increase the efficiency of the sealing function, the cover plate is combined with a sealing ring. The sealing ring is arranged in the axial direction between the cover plate and the row of rolling elements and therefore does not require any additional installation space. The sealing ring runs radially and bridges the radial gap between the bearing outer ring and the bearing inner ring. The sealing ring consists of a solid part, such as a reinforcement, which is partially or completely enclosed by an elastomer part. The sealing ring has a sealing body and a fastening bead in the radial direction, with which it is arranged on the bearing outer ring. On the radially opposite side, the sealing body has a sealing lip which is tangent to the bearing inner ring.
Ist im Betrieb der Lagerinnenring der rotierende Lagerring im Wälzlager, so führt die feste Anbindung der Abdeckscheibe am Lagerinnenring dazu, dass diese mit dem Lagerinnenring mitrotiert. Der Lageraußenring wäre in diesem Fall drehstarr montiert. Durch die Rotation der Abdeckscheibe kann das Wälzlager von umgebenden Medien weitgehend abgeschirmt werden. Die Abdeckscheibe schleudert zuströmende Medien und störende Partikel durch Zentrifugalkraft vom Wälzlager weg und fungiert somit als Schleuderscheibe. Sie hält einen Großteil einströmender Medien fern. Als weitere Instanz zur Abschirmung des Inneren des Wälzlagers fungiert der Dichtung, welcher mit einer Dichtlippe am Lagerinnenring anliegt. Dabei macht die radial ausgerichtete Dichtlippe nicht mit einem Abschnitt der Abdeckscheibe Kontakt, sondern berührt direkt den Lagerinnenring. Die Dichtung ist als reibungsoptimierte Dichtung ausgestaltet und weist an ihrer Dichtlippe eine Oberfläche mit einem geringen Reibkoeffizienten oder auch Eigenschaften auf, welche die Reibung zwischen der Dichtlippe und dem Lagerinnenring reduzieren. Durch die Kombination aus dem Dichtring mit der am Lagerinnenring anliegenden reibungsoptimierten Dichtlippe und der am Lagerinnenring angeordneten Abdeckscheibe können Schmiermedien im Wälzlager gehalten und gleichzeitig störende Partikel an einem Eintritt ins Wälzlager effizient gehindert werden. Im erfindungsgemäßen Wälzlager ist das Lagerinnere unter hohen Drehzahlen effizient abgedichtet und kommt dabei ohne kostenintensive Bauteile und zusätzlichen Platzbedarf in der Wälzlagerumgebung aus. If the bearing inner ring is the rotating bearing ring in the rolling bearing during operation, the fixed connection of the cover plate to the bearing inner ring means that it rotates with the bearing inner ring. The bearing outer ring would be In this case, it is mounted in a rotationally rigid manner. The rotation of the cover plate means that the rolling bearing can be largely shielded from surrounding media. The cover plate uses centrifugal force to throw incoming media and disruptive particles away from the rolling bearing, thus acting as a centrifugal disc. It keeps most incoming media away. The seal, which has a sealing lip on the bearing inner ring, acts as a further means of shielding the interior of the rolling bearing. The radially aligned sealing lip does not make contact with a section of the cover plate, but rather touches the bearing inner ring directly. The seal is designed as a friction-optimized seal and has a surface on its sealing lip with a low coefficient of friction or properties that reduce the friction between the sealing lip and the bearing inner ring. The combination of the sealing ring with the friction-optimized sealing lip on the bearing inner ring and the cover plate arranged on the bearing inner ring means that lubricating media can be kept in the rolling bearing and at the same time disruptive particles can be efficiently prevented from entering the rolling bearing. In the rolling bearing according to the invention, the interior of the bearing is efficiently sealed at high speeds and does not require any costly components or additional space in the rolling bearing environment.
Vorzugsweise weist die Abdeckscheibe Aussparungen auf. In einer bevorzugten Ausführungsform sind die Aussparungen um laufend benachbart zueinander angeordnet. Vorzugsweise sind die Aussparungen an einem dem Lagerinnenring zugewandten Endabschnitt der Abdeckscheibe angeordnet. Die Aussparungen können in Form von Löchern, welche kreisrund, oval oder langlochförmig sind, vorliegen. Es kann sich bei den Aussparungen auch um Schlitze mit unterschiedlicher Erstreckung in ihrem Verlauf handeln. Die Schlitze können in ihrer Grundform gerade oder bogenförmig sein oder aus einer Kombination verschiedener Geometrien bestehen. In einer bevorzugten Ausführungsform sind die Aussparungen in Umlaufrichtung über der Abdeckscheibe verteilt und damit einander benachbart. Die Aussparungen können gleichmäßig oder nach einem chaotischen Muster oder nach einer weiteren Verteilung, welche für einen Anwendungsfall von Vorteil ist, entlang der Abdeckscheibe angeordnet sein. Bevorzugtermaßen befinden sich die Aussparungen an einem Abschnitt der Ab- deckscheibe, welcher sich in dem Drittel der radialen Gesamtlänge der Abdeckscheibe befindet, welches dem Lagerinnenring nächstgelegen ist. Ausgehend vom Lageraußenring handelt es sich hierbei um den Endabschnitt der Abdeckscheibe. Im Betrieb erwärmt sich das Wälzlager und es bildet sich Kondenswasser, welches sich im Wälzlager ansammeln kann und zu einer Schädigung der Dichtung führen kann. Die Aussparungen realisieren eine Entwässerung des Wälzlagers im Betrieb und, bei um laufender Anordnung der Aussparungen, zudem im Ruhezustand des Wälzlagers. Damit werden stehende Medien unterbunden und dadurch bedingte Reaktionen zwischen Medien und der Dichtung zuverlässig verhindert. The cover plate preferably has recesses. In a preferred embodiment, the recesses are arranged adjacent to one another in a continuous manner. The recesses are preferably arranged on an end section of the cover plate facing the bearing inner ring. The recesses can be in the form of holes which are circular, oval or have an elongated hole shape. The recesses can also be slots with different extensions in their course. The slots can be straight or curved in their basic form or consist of a combination of different geometries. In a preferred embodiment, the recesses are distributed in the circumferential direction over the cover plate and thus adjacent to one another. The recesses can be arranged evenly or in a chaotic pattern or in a further distribution which is advantageous for an application along the cover plate. The recesses are preferably located on a section of the cover plate. cover plate, which is located in the third of the total radial length of the cover plate that is closest to the bearing inner ring. Starting from the bearing outer ring, this is the end section of the cover plate. During operation, the rolling bearing heats up and condensation forms, which can collect in the rolling bearing and cause damage to the seal. The recesses allow the rolling bearing to be drained during operation and, if the recesses are arranged all around, also when the rolling bearing is at rest. This prevents stagnant media and reliably prevents reactions between media and the seal caused by this.
Vorzugsweise weist der Dichtring eine weitere Dichtlippe auf, welche mit der Abdeckscheibe Kontakt macht. In einer bevorzugten Ausführungsform ist die weitere Dichtlippe schräg zur Abdeckscheibe ausgerichtet. Bevorzugtermaßen weist der Dichtring zusätzlich zur Dichtlippe, welche mit dem Lagerinnenring in Kontakt steht, eine weitere Dichtlippe auf, welche an der Abdeckscheibe anliegt. In einer bevorzugten Ausführungsform verläuft die weitere Dichtlippe schräg zur Abdeckscheibe. Durch die weitere Dichtlippe werden zwei Kammern gebildet. Ein Spalt zwischen der Abdeckscheibe und einem radialen Innenbord des Lageraußenring, welcher der Abdeckscheibe radial gegenüberliegt, bildet den Eingang zur ersten Kammer. Begrenzt wird die erste Kammer durch die weitere Dichtlippe. Die zweite Kammer befindet sich zwischen der weiteren Dichtlippe, der Dichtlippe und einem Teil der Abdeckscheibe und weist keine Öffnung auf. Partikel, welche die rotierende Abdeckscheibe in ihrer Funktion als Schleuderscheibe passieren, gelangen zunächst in die erste Kammer, wobei die weitere Dichtlippe eine Barriere bildet. Ist die weitere Dichtlippe zudem schräg zur Abdeckscheibe hin mit einer Neigungstendenz zum Lageraußenring ausgeprägt, sammeln sich störende Partikel in einer Rille zwischen der weiteren Dichtlippe und dem Dichtkörper. Durch die Fliehkraft werden die Partikel im Betrieb wieder in Richtung des Lageraußenrings geschleudert. Sollten Partikel dennoch die weitere Dichtlippe überwinden, befinden sie sich noch immer nicht im Inneren des Wälzlagers, sondern erst in der zweiten Kammer, wo die Dichtlippe ein Eindringen ins Wälzlagerinnere unterbindet. Die weitere Dichtlippe weist eine Oberfläche mit einem geringen Reibkoeffizienten oder auch Eigenschaften auf, welche die Reibung zwischen der weiteren Dichtlippe und der Abdeckscheibe reduzieren. Damit macht sich diese Ausführungsform des Wälzlagers hohe Drehzahlen für die Funktionalität einer der beiden Komponenten der Dichtung, nämlich der Abdeckscheibe, zu Nutze. In Kombination mit der zweiten Komponente, einem Dichtung mit einer reibungsoptimierten, am Lagerinnenring anliegenden Dichtlippe und einer weiteren, reibungsoptimierten, an der Abdeckscheibe anliegenden, Dichtlippe kann eine zuverlässige Abdichtung des Wälzlagerinneren bei hoher Energieeffizienz und geringem Bauraum erzielt werden. The sealing ring preferably has a further sealing lip which makes contact with the cover plate. In a preferred embodiment, the further sealing lip is aligned at an angle to the cover plate. In addition to the sealing lip which is in contact with the bearing inner ring, the sealing ring preferably has a further sealing lip which rests on the cover plate. In a preferred embodiment, the further sealing lip runs at an angle to the cover plate. Two chambers are formed by the further sealing lip. A gap between the cover plate and a radial inner edge of the bearing outer ring, which is radially opposite the cover plate, forms the entrance to the first chamber. The first chamber is delimited by the further sealing lip. The second chamber is located between the further sealing lip, the sealing lip and part of the cover plate and has no opening. Particles which pass through the rotating cover plate in its function as a centrifugal disk first reach the first chamber, with the further sealing lip forming a barrier. If the additional sealing lip is also inclined towards the cover plate with a tendency to tilt towards the bearing outer ring, disruptive particles collect in a groove between the additional sealing lip and the sealing body. The centrifugal force causes the particles to be thrown back towards the bearing outer ring during operation. If particles do manage to overcome the additional sealing lip, they are still not inside the rolling bearing, but only in the second chamber, where the sealing lip prevents them from penetrating into the rolling bearing interior. The additional sealing lip has a surface with a low coefficient of friction or properties that reduce the friction between the other sealing lip and the cover plate. This design of the rolling bearing therefore makes use of high speeds for the functionality of one of the two components of the seal, namely the cover plate. In combination with the second component, a seal with a friction-optimized sealing lip that rests on the bearing inner ring and another friction-optimized sealing lip that rests on the cover plate, a reliable seal of the rolling bearing interior can be achieved with high energy efficiency and little installation space.
Vorzugsweise weist die Abdeckscheibe einen schräg zur Wälzkörperreihe hin verlaufenden Abschnitt auf. Bevorzugtermaßen weist die Abdeckscheibe einen Abschnitt auf, welcher weder rein in axiale Richtung noch rein in radiale Richtung, sondern schräg verläuft und dabei hin zur Wälzkörperreihe. Als Referenz für die Richtungsangabe dient ein radial, also senkrecht zur Rotationsachse verlaufender, mittlerer Abschnitt der Abdeckscheibe. Dieser Abschnitt befindet sich radial weder an dem Ende, welches am Lagerinnenring angeordnet ist, noch an dem Ende, welches am Lageraußenring angeordnet ist, sondern in einem mittleren Bereich der Abdeckscheibe. Der mittlere Abschnitt umfasst mindestens das Drittel der Abdeckscheibe, welches auch den Mittelpunkt der Abdeckscheibe in radialer Richtung beinhaltet. Damit ist ein Abschnitt schräg zur Wälzkörperreihe hin verlaufend, wenn er in seinem Verlauf einen geringen axialen Abstand zur einer radial durch den Wälzkörpermittelpunkt verlaufenden Geraden aufweist als der radial verlaufende mittlere Abschnitt. Der schräg zur Wälzkörperreihe hin verlaufende Abschnitt bildet eine Führungsfläche an der Abdeckscheibe. Diese hat zum Ziel, Medien, welche die Abdeckscheibe überwunden haben, zu führen und, gefördert durch die im Betrieb wirkende Zentrifugalkraft, wieder kontrolliert ausaustreten zu lassen. The cover disk preferably has a section that runs diagonally towards the row of rolling elements. The cover disk preferably has a section that runs neither purely in the axial direction nor purely in the radial direction, but rather diagonally towards the row of rolling elements. A middle section of the cover disk that runs radially, i.e. perpendicular to the axis of rotation, serves as a reference for the direction indication. This section is located radially neither at the end that is arranged on the bearing inner ring nor at the end that is arranged on the bearing outer ring, but in a middle area of the cover disk. The middle section comprises at least the third of the cover disk that also contains the center of the cover disk in the radial direction. A section is therefore said to run diagonally towards the row of rolling elements if it has a smaller axial distance to a straight line running radially through the center of the rolling elements than the radially running middle section. The section that runs diagonally towards the row of rolling elements forms a guide surface on the cover disk. The aim of this is to guide media that have overcome the cover plate and, promoted by the centrifugal force acting during operation, to allow them to escape again in a controlled manner.
In einer weiteren bevorzugten Ausführungsform weist die Abdeckscheibe einen parallel zu einem radialen Innenbord des Lageraußenrings verlaufenden Abschnitt und einen C-förmigen Abschnitt auf. Vorzugsweise weist die Abdeck- scheibe einen Abschnitt auf, welcher am Lageraußenring angeordnet ist und axial verläuft. Der Lageraußenring weist auf seiner radial innenliegenden Seite, also auf der den Wälzkörpern zugewandten Seite, eine Begrenzungsfläche auf, einen radialen Innenbord. Parallel zu diesem radialen Innenbord verläuft an einem axialen Ende des Lageraußenrings ein Abschnitt der Abdeckscheibe, wobei zwischen dem radialen Innenbord des Lageraußenrings und der Abdeckscheibe eine Spaltdichtung gebildet wird. Zusätzlich weist die Abdeckscheibe einen C-förmigen Abschnitt auf. Dabei kann die Öffnung des Cs hin zur Wälz- körperreihe, weg von der Wälzkörperreihe oder auch hin zum Lageraußenring oder zum Lagerinnenring orientiert sein. In a further preferred embodiment, the cover plate has a section running parallel to a radial inner rim of the bearing outer ring and a C-shaped section. Preferably, the cover plate disc has a section which is arranged on the bearing outer ring and runs axially. The bearing outer ring has a boundary surface on its radially inner side, i.e. on the side facing the rolling elements, a radial inner rim. A section of the cover disc runs parallel to this radial inner rim at one axial end of the bearing outer ring, with a gap seal being formed between the radial inner rim of the bearing outer ring and the cover disc. The cover disc also has a C-shaped section. The opening of the C can be oriented towards the row of rolling elements, away from the row of rolling elements or towards the bearing outer ring or the bearing inner ring.
Vorzugsweise weist der Lageraußenring und/oder der Lagerinnenring eine ström isolierende Schicht auf. Bevorzugtermaßen weist der Lageraußenring o- der der Lagerinnenring oder der Lagerinnenring und der Lagerinnenring eine Schicht auf, welche keinen Strom leitet. Damit wird ein Stromdurchfluss durch das Wälzlager verhindert, wodurch die Lebensdauer des Wälzlagers erhöht werden kann. Preferably, the bearing outer ring and/or the bearing inner ring have a current-insulating layer. Preferably, the bearing outer ring or the bearing inner ring or the bearing inner ring and the bearing inner ring have a layer that does not conduct electricity. This prevents current from flowing through the rolling bearing, which can increase the service life of the rolling bearing.
Bevorzugtermaßen weist die Abdeckscheibe am Lagerinnenring einen C- förmigen Abschnitt mit um laufend zueinander benachbarten Aussparungen auf, wobei auf den C-förmigen Abschnitt ein Abschnitt folgt, welcher, ausgehend von einem radial verlaufenden mittleren Abschnitt, schräg zur Wälzkörperreihe hin verläuft, wobei sich an diesen schräg zur Wälzkörperreihe hin verlaufenden Abschnitt der radial verlaufende mittlere Abschnitt anschließt, welchem ein schräg zur Wälzkörperreihe hin verlaufender Abschnitt folgt und wobei die Abdeckscheibe im Bereich des Lageraußenrings einen parallel zu einem radialen Innenbord des Lageraußenrings verlaufenden Abschnitt aufweist. Vorzugsweise gliedert sich die Abdeckscheibe in verschiedene Abschnitte. In einem mittleren Abschnitt weist die Abdeckscheibe einen Verlauf in radialer Richtung auf und verläuft geradlinig. Ausgehend von diesem mittleren, radial verlaufenden Abschnitt weist die Abdeckscheibe radial beiderseits je einen Abschnitt auf, welcher schräg verläuft und in Richtung der Wälzkörperreihe orientiert ist. Die schräg verlaufenden Abschnitte laufen also schräg von dem mittleren Abschnitt weg und hin zur Wälzkörperreihe und verringern damit den axialen Abstand zur Wälzkörperreihe. In Richtung des Lagerinnenrings schließt sich ein Abschnitt in Form eines Cs an, welcher an einem zum Außenring hin orientierten Bord des Lagerinnenrings anliegt. Auf der radial gegenüberliegenden Seite schließt sich dem schräg zur Wälzkörperreihe hin verlaufenden Abschnitt ein weiterer Abschnitt an, welcher in einem parallel zu einem radialen Innenbord des Lageraußenrings verlaufenden Abschnitt ausläuft. Zwischen dem radialen Innenbord des Lageraußenrings und der Abdeckscheibe wird damit eine Spaltdichtung ausgebildet. Preferably, the cover disk on the bearing inner ring has a C-shaped section with adjacent recesses all the way around, the C-shaped section being followed by a section which, starting from a radially running central section, runs diagonally towards the row of rolling elements, this section running diagonally towards the row of rolling elements being followed by the radially running central section, which is followed by a section running diagonally towards the row of rolling elements, and the cover disk in the area of the bearing outer ring having a section running parallel to a radial inner rim of the bearing outer ring. Preferably, the cover disk is divided into different sections. In a central section, the cover disk runs in a radial direction and runs in a straight line. Starting from this central, radially running section, the cover disk has a section on each side radially which runs diagonally and is oriented in the direction of the row of rolling elements. The diagonally running sections therefore run diagonally from the central section away and towards the row of rolling elements, thereby reducing the axial distance to the row of rolling elements. In the direction of the inner bearing ring, there is a section in the shape of a C, which rests against a rim of the inner bearing ring oriented towards the outer ring. On the radially opposite side, the section running diagonally towards the row of rolling elements is followed by another section, which ends in a section running parallel to a radial inner rim of the outer bearing ring. A gap seal is thus formed between the radial inner rim of the outer bearing ring and the cover plate.
Kurze Beschreibung der Zeichnungen Short description of the drawings
Die Erfindung wird nachfolgend anhand von Ausführungsbeispielen unter Bezugnahme auf die Zeichnungen erläutert. Die Zeichnungen sind schematische Darstellung und zeigen in: The invention is explained below using embodiments with reference to the drawings. The drawings are schematic representations and show in:
Figur 1 eine Prinzipdarstellung des erfindungsgemäßen Wälzlagers in einer perspektivischen Ansicht, Figure 1 is a schematic diagram of the rolling bearing according to the invention in a perspective view,
Figur 2 eine Prinzipdarstellung einer Ausführungsform des erfindungsgemäßen Wälzlagers in einer geschnittenen Teilansicht,Figure 2 shows a schematic diagram of an embodiment of the rolling bearing according to the invention in a sectional partial view,
Figur 3 eine Prinzipdarstellung einer weiteren Ausführungsform des erfindungsgemäßen Wälzlagers in einer geschnittenen Teilansicht. Figure 3 is a schematic diagram of another embodiment of the rolling bearing according to the invention in a partial sectional view.
Ausführliche Beschreibung der Zeichnungen Detailed description of the drawings
Figur 1 zeigt eine perspektivische Ansicht eines als Kugellager ausgebildeten erfindungsgemäßen Wälzlagers 1 . Dabei ist in axialer Richtung a verlaufend in Richtung der Rotationsachse 2 verlaufend. In radialer Richtung r verlaufend ist senkrecht zur Rotationsachse 2 verlaufend. Das Wälzlager 1 setzt sich zusammen aus einem um eine Rotationsachse 2 angeordneten Lagerinnenring 5 und einem konzentrisch dazu angeordneten Lageraußenring 3 größeren Durchmessers. Zwischen Lageraußenring 3 und Lagerinnenring 5 ist in radialer Richtung r ein Spalt, also ein Radialspalt, gebildet. Dieser Radialspalt wird durch eine Ab- deckscheibe 10 überbrückt, welche umlaufend ist und sich in radiale Richtung r vom Lagerinnenring 5 zum Lageraußenring 3 erstreckt. Die Abdeckscheibe 10 ist in radiale Richtung r nicht plan, sondern weist Erhöhungen und Senken auf und ist damit in verschiedene Abschnitte unterteilt. Angrenzend an den Lagerinnenring 5 weist die Abdeckscheibe 10 einen Endabschnitt 15 auf. Der Endabschnitt 15 weist um laufend gleichmäßig verteilte Aussparungen 14 auf, welche teilkreisförmig ausgebildet sind. Die Aussparungen 14 ermöglichen eine Entwässerung des Wälzlagers 1 sowohl im laufenden Betrieb als auch im Ruhezustand. Figure 1 shows a perspective view of a rolling bearing 1 according to the invention designed as a ball bearing. In the axial direction a, the direction of the rotation axis 2 is in the direction of the rotation axis 2. In the radial direction r, the direction of the rotation axis 2 is perpendicular to the rotation axis 2. The rolling bearing 1 is composed of a bearing inner ring 5 arranged around a rotation axis 2 and a bearing outer ring 3 of larger diameter arranged concentrically thereto. A gap, i.e. a radial gap, is formed between the bearing outer ring 3 and the bearing inner ring 5 in the radial direction r. This radial gap is formed by a cover disk 10, which is circumferential and extends in the radial direction r from the bearing inner ring 5 to the bearing outer ring 3. The cover disk 10 is not flat in the radial direction r, but has elevations and depressions and is thus divided into different sections. Adjacent to the bearing inner ring 5, the cover disk 10 has an end section 15. The end section 15 has recesses 14 that are evenly distributed all around and are designed in the shape of a part circle. The recesses 14 enable drainage of the rolling bearing 1 both during operation and when at rest.
Figur 2 zeigt eine geschnittene Teilansicht einer Ausführungsform des erfindungsgemäßen Wälzlagers 1. Das Wälzlager 1 ist als Kugellager ausgebildet mit einem um eine Rotationsachse 2 angeordneten Lagerinnenring 5 und einem konzentrisch dazu angeordneten Lageraußenring 3, zwischen welchen in radiale Richtung r, also senkrecht zur Rotationsachse 2, ein Radialspalt ausgebildet ist. Der Lageraußenring 3 weist eine erste Laufbahn 4 für Wälzkörper 8 auf. Der ihm in radialer Richtung r gegenüberliegende Lagerinnenring 5 weist eine zweite Laufbahn 6 für Wälzkörper 8 auf. Ein Käfig 7 führt die Wälzkörper 8 drehbar auf den Laufbahnen 4, 6 in einer Wälzkörperreihe 9. Der Lageraußenring 3 weist einen radialen Innenbord 12 am Lageraußenring 3 auf. Dieser verläuft in axialer Richtung a, also entlang der Rotationsachse 2, und reduziert sprunghaft seine radiale Erstreckung. Der radiale Innenbord 12 bildet eine erste Nut 21 aus und verläuft dann weiter zu einem axialen Ende des Wälzlagers 1 . Dem radialen Innenbord 12 des Lageraußenrings 3 liegt in radialer Richtung r ein radialer Innenbord 23 des Lagerinnenrings 5 gegenüber. Dieser verläuft in axialer Richtung a und reduziert sprunghaft seine radiale Erstreckung. Der radiale Innenbord 23 bildet eine zweite Nut 22 aus und verläuft dann weiter zu einem axialen Ende des Wälzlagers 1 . Direkt benachbart zur Wälzkörperreihe 9 ist an der ersten Nut 21 ein Dichtring 11 angeordnet, welcher sich radial bis zum Lagerinnenring 5 erstreckt. Der Dichtring 11 weist eine Dichtlippe 13 auf, welche den radialen Innenbord 23 des Lagerinnenrings 5 kontaktiert. In axialer Richtung a benachbart zum Dichtring 11 ist an der zweiten Nut 22 eine Abdeckscheibe 10 angeordnet. Diese überbrückt den zwischen Lagerinnenring 5 und Lageraußen- ring 3 gebildeten Radialspalt, wobei zwischen der Abdeckscheibe 10 und dem radialen Innenbord 12 des Lageraußenrings 3 ein Spalt verbleibt. An einem Endabschnitt 15 der Abdeckscheibe 10, welcher am Lagerinnenring 5 angeordnet ist, weist die Abdeckscheibe 10 Aussparungen 14 auf. Die Aussparungen 14 setzten eine Entwässerung des Wälzlagers 1 sowohl im Stillstand als auch im Betrieb um. Die Abdeckscheibe 10 setzt sich aus verschiedenen Abschnitten 17, 18, 19, 20 zusammen. Am Lagerinnenring 5 weist die Abdeckscheibe 10 einen C-förmigen Abschnitt 20 auf, im mittleren Bereich einen radialen mittleren Abschnitt 19, welcher in radialer Richtung r verläuft. Ausgehend vom radialen mittleren Abschnitt 19 schließt sich beidseitig je ein Abschnitt 17 an, welcher schräg zur Wälzkörperreihe 9 hin verläuft. Am radialen Innenbord 12 des Lageraußenrings 3 weist die Abdeckscheibe 10 einen Abschnitt 18 auf, welcher parallel zum radialen Innenbord 12 verläuft. Figure 2 shows a sectional partial view of an embodiment of the rolling bearing 1 according to the invention. The rolling bearing 1 is designed as a ball bearing with a bearing inner ring 5 arranged around a rotation axis 2 and a bearing outer ring 3 arranged concentrically thereto, between which a radial gap is formed in the radial direction r, i.e. perpendicular to the rotation axis 2. The bearing outer ring 3 has a first raceway 4 for rolling elements 8. The bearing inner ring 5 opposite it in the radial direction r has a second raceway 6 for rolling elements 8. A cage 7 guides the rolling elements 8 so that they can rotate on the raceways 4, 6 in a row of rolling elements 9. The bearing outer ring 3 has a radial inner rim 12 on the bearing outer ring 3. This runs in the axial direction a, i.e. along the rotation axis 2, and abruptly reduces its radial extent. The radial inner rim 12 forms a first groove 21 and then continues to an axial end of the rolling bearing 1. A radial inner rim 23 of the bearing inner ring 5 is located opposite the radial inner rim 12 of the bearing outer ring 3 in the radial direction r. This runs in the axial direction a and abruptly reduces its radial extent. The radial inner rim 23 forms a second groove 22 and then continues to an axial end of the rolling bearing 1. A sealing ring 11 is arranged on the first groove 21 directly adjacent to the row of rolling elements 9 and extends radially to the bearing inner ring 5. The sealing ring 11 has a sealing lip 13 which contacts the radial inner rim 23 of the bearing inner ring 5. A cover disk 10 is arranged on the second groove 22 adjacent to the sealing ring 11 in the axial direction a. This bridges the gap between the bearing inner ring 5 and the bearing outer ring. ring 3, whereby a gap remains between the cover disk 10 and the radial inner rim 12 of the bearing outer ring 3. At an end section 15 of the cover disk 10, which is arranged on the bearing inner ring 5, the cover disk 10 has recesses 14. The recesses 14 implement drainage of the rolling bearing 1 both when stationary and during operation. The cover disk 10 is made up of various sections 17, 18, 19, 20. On the bearing inner ring 5, the cover disk 10 has a C-shaped section 20, in the middle area a radial middle section 19, which runs in the radial direction r. Starting from the radial middle section 19, a section 17 adjoins both sides, which runs at an angle to the row of rolling elements 9. On the radial inner rim 12 of the bearing outer ring 3, the cover disk 10 has a section 18 which runs parallel to the radial inner rim 12.
Im laufenden Betrieb rotiert der Lagerinnenring 5 mit der dort angeordneten Abdeckscheibe 10. Der Dichtring 11 bleibt statisch wie auch der Lageraußenring 3. Axial, auf der Seite der Abdeckscheibe 10 einströmende Medien und Verunreinigungen prallen von den Abdeckscheibe 10 ab, beziehungsweise werden durch Zentrifugalkraft von der Abdeckscheibe 10 weggeschleudert. Medien sowie störende Partikel, welche an der Abdeckscheibe 10 vorbeigelangen, werden durch den in das Wälzlager 1 integrierten Dichtring 11 an einem Eintritt ins Innere des Wälzlagers 1 gehindert. Im Ruhezustand des Wälzlagers 1 kann Medium wie Kondenswasser, welches sich im Betrieb bildet, durch die Aussparungen 14 an der Abdeckscheibe 10 austreten. Damit werden stehende Medien am Dichtring 11 vermieden, welche eine Schädigung des Dichtrings 11 und damit dessen frühzeitiges Versagen begünstigen würden. Auch im laufenden Betrieb ermöglichen die Aussparungen 14 durch ihre umlaufende Anordnung eine Entwässerung des Wälzlagers 1. Die lagerintegrierte Kombination bestehend aus dem Dichtring 11 und der Abdeckscheibe 10 mit Aussparungen 14 ermöglicht eine effiziente Abdichtung des Inneren des Wälzlagers 1 bei geringem Bauraum und ohne zusätzliche Komponenten. Das Wälzlager 1 kann damit als Ganzes, platzsparend und wirtschaftlich montiert werden. Figur 3 zeigt eine weitere Ausführungsform eines erfindungsgemäßen Wälzlagers 1 in einer geschnittenen Teilansicht. Das Wälzlager 1 ist analog zum Wälzlager 1 aus Figur 2 um eine in axiale Richtung a verlaufende Rotationsachse 2 angeordnet und weist einen Lageraußenring 3 mit erster Laufbahn 4, einen Lagerinnenring 5 mit zweiter Laufbahn 6, Wälzkörper 8 in einer Wälzkörperreihe 9, geführt durch einen Käfig 7 auf. Eine radiale Richtung r ist senkrecht zur Rotationsachse 2 ausgerichtet. Ein radialer Innenbord 12 des Lageraußenrings 3 ist analog zu Figur 2 ausgeführt und weist eine erste Nut 21 auf. Der Lagerinnenrings 5 weist einen radialen Innenbord 23 mit einer zweiten Nut 22 auf. An der ersten Nut 21 ist ein Dichtring 11 angeordnet, an der zweiten Nut 22 eine Abdeckscheibe 10. Im Unterschied zu Figur 2 weist der Dichtring 11 zusätzlich zu einer Dichtlippe 13, welche am Lagerinnenring 5 schleift, eine weitere Dichtlippe 16 auf, aber keine Öffnungen zur Entwässerung. Die weitere Dichtlippe 16 entspringt dem Dichtring 11 , verläuft zur Rotationsachse 2 geneigt schräg zur Abdeckscheibe 10 hin und kontaktiert die Abdeckscheibe 10 auf der der Wälzkörperreihe 9 zugewandten Seite. Die Abdeckscheibe 10 ist analog zu Figur 2 am Lagerinnenring 5 angeordnet und in mehrere Abschnitte 17, 18, 19, 20 unterteilt. Sie weist einen parallel zum radialen Innenbord 12 des Lageraußenrings 3 verlaufenden Abschnitt 18, einen mittleren radial verlaufenden Abschnitt 19, einen C-förmigen Abschnitt 20 auf sowie Abschnitte 17, welche schräg zur Wälz- körperreihe 9 hin verlaufen. Durch die weitere Dichtlippe 16 wird eine zusätzliche Hürde geschaffen, umgebende Medien von einem Eintritt ins Innere des Wälzlagers 1 abzuhalten. Medien, welche sich im Inneren des Wälzlagers 1 befinden und dort verbleiben sollen, wie Schmiermedien, werden durch die weitere Dichtlippe 16 innen gehalten. Im laufenden Betrieb wird auftreffendes Medium durch die gemeinsam mit dem Lagerinnenring 5 rotierenden Abdeckscheibe 10 weggeschleudert. Partikel, die dennoch durch den verbleibenden Spalt zwischen Abdeckscheibe 10 und radialem Innenbord 12 des Lageraußenrings 3 eindringen, werden von der weiteren Dichtlippe 16 am Dichtring 11 abgefangen. Sollten im Laufe des Betriebs Medien die weitere Dichtlippe 16 passieren, verbleibt die Dichtlippe 13 als weitere Instanz, um auch diese Medien von einem Eintritt ins Innere des Wälzlagers 1 abzuhalten. Damit wird die Dichteffizienz weiter erhöht und das Innere des Wälzlagers 1 auch bei hohen Drehzahlen zuverlässig abgedichtet. During operation, the bearing inner ring 5 rotates with the cover plate 10 arranged there. The sealing ring 11 remains static, as does the bearing outer ring 3. Media and contaminants flowing in axially on the side of the cover plate 10 bounce off the cover plate 10 or are thrown away from the cover plate 10 by centrifugal force. Media and disruptive particles that get past the cover plate 10 are prevented from entering the interior of the rolling bearing 1 by the sealing ring 11 integrated into the rolling bearing 1. When the rolling bearing 1 is at rest, media such as condensation water that forms during operation can escape through the recesses 14 on the cover plate 10. This prevents stagnant media on the sealing ring 11, which would damage the sealing ring 11 and thus cause it to fail prematurely. Even during operation, the recesses 14 allow drainage of the rolling bearing 1 due to their circumferential arrangement. The bearing-integrated combination consisting of the sealing ring 11 and the cover plate 10 with recesses 14 enables efficient sealing of the interior of the rolling bearing 1 with little installation space and without additional components. The rolling bearing 1 can thus be installed as a whole, in a space-saving and economical manner. Figure 3 shows a further embodiment of a rolling bearing 1 according to the invention in a sectional partial view. The rolling bearing 1 is arranged analogously to the rolling bearing 1 from Figure 2 around a rotation axis 2 running in the axial direction a and has a bearing outer ring 3 with a first raceway 4, a bearing inner ring 5 with a second raceway 6, rolling elements 8 in a row of rolling elements 9, guided by a cage 7. A radial direction r is aligned perpendicular to the rotation axis 2. A radial inner rim 12 of the bearing outer ring 3 is designed analogously to Figure 2 and has a first groove 21. The bearing inner ring 5 has a radial inner rim 23 with a second groove 22. A sealing ring 11 is arranged on the first groove 21, and a cover disk 10 on the second groove 22. In contrast to Figure 2, the sealing ring 11 has a further sealing lip 16 in addition to a sealing lip 13 which rubs against the bearing inner ring 5, but no openings for drainage. The further sealing lip 16 originates from the sealing ring 11, runs inclined to the rotation axis 2 at an angle to the cover disk 10 and contacts the cover disk 10 on the side facing the row of rolling elements 9. The cover disk 10 is arranged on the bearing inner ring 5 in a similar way to Figure 2 and is divided into several sections 17, 18, 19, 20. It has a section 18 running parallel to the radial inner rim 12 of the bearing outer ring 3, a middle radial section 19, a C-shaped section 20 and sections 17 which run at an angle to the row of rolling elements 9. The additional sealing lip 16 creates an additional hurdle to prevent surrounding media from entering the interior of the rolling bearing 1. Media which are located inside the rolling bearing 1 and are intended to remain there, such as lubricating media, are held inside by the additional sealing lip 16. During operation, any medium which hits it is thrown away by the cover disk 10 which rotates together with the bearing inner ring 5. Particles which nevertheless penetrate through the remaining gap between the cover disk 10 and the radial inner rim 12 of the bearing outer ring 3 are intercepted by the additional sealing lip 16 on the sealing ring 11. If media pass through the additional sealing lip 16 during operation, the sealing lip 13 remains as an additional instance to prevent these media from entering the interior of the rolling bearing 1. This increases the sealing efficiency further increased and the interior of the rolling bearing 1 is reliably sealed even at high speeds.
Bezugszeichenliste List of reference symbols
1 Wälzlager 1 rolling bearing
Rotationsachse Rotation axis
3 Lageraußenring 3 Bearing outer ring
4 erste Laufbahn 4 first career
5 Lagerinnenring 5 Bearing inner ring
6 zweite Laufbahn 6 second career
7 Käfig 7 Cage
8 Wälzkörper 8 rolling elements
9 Wälzkörperreihe 9 Rolling element row
10 Abdeckscheibe 10 Cover plate
11 Dichtung 11 Seal
12 radialer Innenbord des Lageraußenrings12 radial inboard of the bearing outer ring
13 Dichtlippe 13 Sealing lip
14 Aussparung 14 Recess
15 Endabschnitt der Abdeckscheibe 15 End section of the cover plate
16 weitere Dichtlippe 16 additional sealing lips
17 Abschnitt der Abdeckscheibe 17 Section of the cover plate
18 Abschnitt der Abdeckscheibe 18 Section of the cover plate
19 Abschnitt der Abdeckscheibe 19 Section of the cover plate
20 Abschnitt der Abdeckscheibe 20 Section of the cover plate
21 erste Nut 21 first groove
22 zweite Nut 22 second groove
23 radialer Innenbord des Lagerinnenrings a axiale Richtung r radiale Richtung 23 radial inboard of the bearing inner ring a axial direction r radial direction

Claims

Patentansprüche Patent claims
1 . Wälzlager (1 ) mit einem um eine in axiale Richtung (a) verlaufende Rotationsachse (2) angeordneten Lageraußenring (3), welcher eine erste Laufbahn (4) aufweist, und einem konzentrisch dazu angeordneten Lagerinnenring (5), welcher eine, der ersten Laufbahn (3) in radiale Richtung (r) gegenüberliegende zweite Laufbahn (6) aufweist, mit einem Käfig (7), welcher auf den Laufbahnen (3, 6) abrollende Wälzkörper (8) in einer Wälzkörperreihe (9) drehbar führt, sowie einer Abdeckscheibe (10) und einem Dichtung (11 ), welche beide radial zwischen dem Lagerinnring (5) und dem Lageraußenring (3) angeordnet sind, dadurch gekennzeichnet, dass die Abdeckscheibe (10) am Lagerinnenring (5) angebracht ist und der Dichtring (11 ) axial zwischen der Wälzkörperreihe (9) und der Abdeckscheibe (10) angeordnet ist und eine Dichtlippe (13) aufweist, welche mit dem Lagerinnenring (5) Kontakt macht. 1. Rolling bearing (1) with a bearing outer ring (3) arranged about a rotation axis (2) running in the axial direction (a), which has a first raceway (4), and a bearing inner ring (5) arranged concentrically thereto, which has a second raceway (6) opposite the first raceway (3) in the radial direction (r), with a cage (7) which rotatably guides rolling elements (8) rolling on the raceways (3, 6) in a row of rolling elements (9), and with a cover disk (10) and a seal (11), both of which are arranged radially between the bearing inner ring (5) and the bearing outer ring (3), characterized in that the cover disk (10) is attached to the bearing inner ring (5) and the sealing ring (11) is arranged axially between the row of rolling elements (9) and the cover disk (10) and has a sealing lip (13) which makes contact with the bearing inner ring (5).
2. Wälzlager (1 ) nach Anspruch 1 , dadurch gekennzeichnet, dass die Abdeckscheibe (10) Aussparungen (14) aufweist. 2. Rolling bearing (1) according to claim 1, characterized in that the cover plate (10) has recesses (14).
3. Wälzlager (1 ) nach Anspruch 2, dadurch gekennzeichnet, dass die Aussparungen (14) umlaufend benachbart zueinander angeordnet sind. 3. Rolling bearing (1) according to claim 2, characterized in that the recesses (14) are arranged circumferentially adjacent to one another.
4. Wälzlager (1 ) nach Anspruch 2, dadurch gekennzeichnet, dass die Aussparungen (14) an einem dem Lagerinnenring (5) zugewandten Endabschnitt (15) der Abdeckscheibe (10) angeordnet sind. 4. Rolling bearing (1) according to claim 2, characterized in that the recesses (14) are arranged on an end portion (15) of the cover plate (10) facing the bearing inner ring (5).
5. Wälzlager (1 ) nach Anspruch 1 , dadurch gekennzeichnet, dass der Dichtring (11 ) eine weitere Dichtlippe (16) aufweist, welche mit der Abdeckscheibe (10) Kontakt macht. 5. Rolling bearing (1) according to claim 1, characterized in that the sealing ring (11) has a further sealing lip (16) which makes contact with the cover plate (10).
6. Wälzlager (1 ) nach Anspruch 5, dadurch gekennzeichnet, dass die weitere Dichtlippe (16) schräg zur Abdeckscheibe (10) ausgerichtet ist. 6. Rolling bearing (1) according to claim 5, characterized in that the further sealing lip (16) is aligned obliquely to the cover plate (10).
7. Wälzlager (1 ) nach Anspruch 1 , dadurch gekennzeichnet, dass die Abdeckscheibe (11 ) einen schräg zur Wälzkörperreihe (9) hin verlaufenden Abschnitt (17) aufweist. 7. Rolling bearing (1) according to claim 1, characterized in that the cover disk (11) has a section (17) running obliquely towards the row of rolling elements (9).
8. Wälzlager (1 ) nach Anspruch 7, dadurch gekennzeichnet, dass die Abdeckscheibe (10) einen parallel zu einem radialen Innenbord (12) des Lageraußenrings (3) verlaufenden Abschnitt (18) und einen C-förmigen Abschnitt (20) aufweist. 8. Rolling bearing (1) according to claim 7, characterized in that the cover disk (10) has a section (18) running parallel to a radial inner rim (12) of the bearing outer ring (3) and a C-shaped section (20).
9. Wälzlager (1 ) nach Anspruch 1 , dadurch gekennzeichnet, dass der Lageraußenring (3) und/oder der Lagerinnenring (5) eine ström isolierende Schicht aufweist. 9. Rolling bearing (1) according to claim 1, characterized in that the bearing outer ring (3) and/or the bearing inner ring (5) has a flow-insulating layer.
10. Wälzlager (1 ) nach Anspruch 1 , dadurch gekennzeichnet, dass die Abdeckscheibe (11 ) am Lagerinnenring (5) einen C-förmigen Abschnitt (20) mit umlaufend zueinander benachbarten Aussparungen (14) aufweist, wobei auf den C-förmigen Abschnitt (20) ein Abschnitt (17) folgt, welcher, ausgehend von einem radial verlaufenden mittleren Abschnitt (19), schräg zur Wälzkörperreihe (9) hin verläuft, wobei sich an diesen schräg zur Wälzkörperreihe (9) hin verlaufenden Abschnitt (17) der radial verlaufende mittlere Abschnitt (19) anschließt, welchem ein schräg zur Wälz- körperreihe (9) hin verlaufender Abschnitt (17) folgt und dass die Abdeckscheibe (10) im Bereich des Lageraußenrings (3) einen parallel zu einem radialen Innenbord (12) des Lageraußenrings (3) verlaufenden Abschnitt (18) aufweist. 10. Rolling bearing (1) according to claim 1, characterized in that the cover disk (11) on the bearing inner ring (5) has a C-shaped section (20) with circumferentially adjacent recesses (14), wherein the C-shaped section (20) is followed by a section (17) which, starting from a radially extending central section (19), runs obliquely towards the row of rolling elements (9), wherein this section (17) running obliquely towards the row of rolling elements (9) is followed by the radially extending central section (19), which is followed by a section (17) running obliquely towards the row of rolling elements (9), and that the cover disk (10) in the region of the bearing outer ring (3) has a section (18) running parallel to a radial inner rim (12) of the bearing outer ring (3).
PCT/DE2023/100681 2022-10-24 2023-09-13 Rolling bearing WO2024088461A1 (en)

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005055039A1 (en) * 2005-11-18 2007-05-24 Schaeffler Kg Antifriction bearing for device which has two components rotating against each other, has caps which have reduced contact area for reducing heat transfer between outer ring and connecting component
WO2010054890A1 (en) 2008-11-13 2010-05-20 Schaeffler Technologies Gmbh & Co. Kg Sealing arrangement having a radial sealing lip
US8061901B2 (en) * 2008-08-22 2011-11-22 Baldor Electric Company Extension member for a flinger of a bearing
DE102017110414A1 (en) * 2016-05-18 2017-11-23 Jtekt Corporation wheel bearing device
DE102018123495A1 (en) 2018-09-25 2020-03-26 Schaeffler Technologies AG & Co. KG Reduced friction ball bearing with centrifugal disc
US20210348646A1 (en) 2020-05-06 2021-11-11 Aktiebolaget Skf Hub bearing assembly for discs for soil cultivation
US20220003319A1 (en) 2020-07-01 2022-01-06 BRUSS Sealing Systems GmbH Seal arrangement and method for manufacturing a seal arrangement

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11257360A (en) 1998-01-07 1999-09-21 Nippon Seiko Kk Rolling bearing with seal ring and automobile transmission
JP2006234081A (en) 2005-02-25 2006-09-07 Ntn Corp Sealed rolling bearing
KR20080100269A (en) 2006-03-08 2008-11-14 에누티에누 가부시키가이샤 Rolling bearing and method for manufacturing the same
DE102009021470A1 (en) 2009-05-15 2010-11-18 Schaeffler Technologies Gmbh & Co. Kg Sealing arrangement for a rolling bearing
JP2019206990A (en) 2018-05-29 2019-12-05 日本精工株式会社 Hub unit bearing with sealing device
DE102020112044A1 (en) 2020-05-05 2021-11-11 Schaeffler Technologies AG & Co. KG Rolling bearing with flinger
CN112709754A (en) 2020-12-31 2021-04-27 八环轴承（长兴）有限公司 Heavy-load waterproof ball bearing

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005055039A1 (en) * 2005-11-18 2007-05-24 Schaeffler Kg Antifriction bearing for device which has two components rotating against each other, has caps which have reduced contact area for reducing heat transfer between outer ring and connecting component
US8061901B2 (en) * 2008-08-22 2011-11-22 Baldor Electric Company Extension member for a flinger of a bearing
WO2010054890A1 (en) 2008-11-13 2010-05-20 Schaeffler Technologies Gmbh & Co. Kg Sealing arrangement having a radial sealing lip
DE102017110414A1 (en) * 2016-05-18 2017-11-23 Jtekt Corporation wheel bearing device
DE102018123495A1 (en) 2018-09-25 2020-03-26 Schaeffler Technologies AG & Co. KG Reduced friction ball bearing with centrifugal disc
US20210348646A1 (en) 2020-05-06 2021-11-11 Aktiebolaget Skf Hub bearing assembly for discs for soil cultivation
US20220003319A1 (en) 2020-07-01 2022-01-06 BRUSS Sealing Systems GmbH Seal arrangement and method for manufacturing a seal arrangement

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