CN110966309A

CN110966309A - Bearing seals and their applications

Info

Publication number: CN110966309A
Application number: CN201811135831.4A
Authority: CN
Inventors: 安德鲁·丹尼尔斯; 孟晓慧; 刘杰; 赵文龙
Original assignee: ZHEJIANG XINCHANG PEER BEARING CO Ltd; Peer Bearing Co
Current assignee: ZHEJIANG XINCHANG PEER BEARING CO Ltd; Peer Bearing Co
Priority date: 2018-09-28
Filing date: 2018-09-28
Publication date: 2020-04-07
Also published as: MY203109A

Abstract

The invention provides a non-contact double-layer sealing element (50) for a rolling bearing, which comprises an inner retainer ring (10) and an outer retainer ring (20) which are sequentially distributed from inside to outside in the axial direction, wherein an axial gap (delta) is formed between the two retainer rings (10, 20)₃). Wherein the inner race (10) is fastened by its base (11) to one of the inner and outer races (1, 2) of the bearing, with its radial free end (13) forming a radial gap (δ) of the inner race with the radially opposite component (1, 2, 21)₁) (ii) a The outer collar (20) is fastened by its base (21) to the other of the inner and outer rings (1, 2) of the bearing, with its radial free end (23) forming a radial gap (delta) of the outer collar with the radially opposite component (1, 2, 11)₂). The invention also provides a deep groove ball bearing adopting the sealing element (50).

Description

Bearing seal and use thereof

Technical Field

The invention relates to a non-contact double-layer sealing element and a rolling bearing applying the sealing element.

Background

Non-contact seals have found widespread use in the field of bearings because of their frictionless, moment-free behavior. In a conventional Deep Groove Ball Bearing (Deep Groove Bearing)100 shown in fig. 1, a retainer ring 5 is fitted in a mounting Groove (aligning Groove)24 of a Bearing outer race 2 through an anchoring (root) portion 11 thereof, with a clearance formed between a free end 13 thereof and an outer surface of the Bearing inner race 1. The single-layer non-contact retainer ring has poor protection effect and is difficult to adapt to the application condition of severe pollution. Although contact seals with sealing lips can achieve a better sealing effect, the resulting frictional torque and temperature rise effects are often not tolerable for many applications. This fact calls for a non-contact seal that has an improved sealing effect without causing friction.

Disclosure of Invention

In order to solve the technical problem, the invention provides a non-contact double-layer sealing element, which comprises an inner retainer ring and an outer retainer ring which are sequentially distributed from inside to outside in the axial direction, wherein an axial gap delta is formed between the two retainer rings₃. Wherein the inner retainer ring is fixed on one of the inner ring and the outer ring of the bearing through the base part thereof, and a radial clearance delta of the inner retainer ring is formed between the radial free end thereof and a part which is positioned opposite to the radial free end in the radial direction₁(ii) a The outer collar is fixed by its base to the other of the inner and outer races of the bearing, with its radial free end forming a radial gap delta of the outer collar with the component situated radially opposite it₂。

Radial clearance delta of the inner retainer ring₁Radial clearance delta of outer retainer ring₂And axial clearance delta between two retaining rings₃The labyrinth clearance channel is formed by connecting in series, the sealing effect of the bearing is greatly improved, the service life of the bearing is greatly prolonged, and the labyrinth clearance channel has great technical advantages compared with a single-layer check ring.

On the basis of the sealing element, the invention also provides the deep groove ball bearing, when the standard boundary size is adopted, the existing deep groove ball bearing with the single-layer retainer ring can be simply replaced, and the deep groove ball bearing has wide application prospect.

Various embodiments and advantages of the present invention are described in detail below with reference to the drawings, wherein like or similar elements are given like reference numerals.

Drawings

FIG. 1 is a schematic cross-sectional view of a conventional deep groove ball bearing using a single-layer retainer ring;

FIG. 2 is a schematic cross-sectional view of a deep groove ball bearing employing the seal of the present invention;

FIG. 3 is an enlarged view of a portion of area A of FIG. 2; and

fig. 4 is a partially enlarged view of a region a in another embodiment of the present invention.

Detailed Description

For the purpose of convenience of description, the direction shown by the axis of the bearing (the chain line in the drawing) is defined as "axial direction", the direction perpendicular to the axis is defined as "radial direction", and a plane on the bearing taken by an imaginary plane containing the axis is defined as "cross section". In the description herein, the spatial position defined by the inner region of the bearing is defined as "inner" and the spatial position defined by the outer region is defined as "outer".

As shown in fig. 2 and 3, the present invention is directed to the use of a double layer seal 50 on both axial sides of the bearing 100. The double seal 50 comprises an inner cage 10 facing the rolling elements 3 and an outer cage 20 located axially outside the inner cage 10. An axial gap delta is formed between the two

retaining rings

10 and 20₃So as not to interfere with each other. Alternatively, the inner and outer retainers may be stamped from sheet steel and then galvanized or may be stamped directly from galvanized sheet steel.

In the embodiment of fig. 3, the inner retainer 10 is identical to the single-layer retainer 5 of fig. 1 except that its mounting groove 24 is located axially away from the edge of the bearing outer race 2 (offset towards the belly of the outer race 2) to allow the outer retainer 20 the necessary axial space.

In the embodiment shown in fig. 3, the outer retainer 20 is formed to have a substantially L-shaped cross section, including an axially extending portion 21 extending in the axial direction and a radially extending portion 22 extending in the radial direction. Wherein the radial extension 22 is turned axially inwards to form the axial extension 21. As a root of the outer collar 20, the axial extension 21 fastens the outer collar 20 to the inner ring 1 of the bearing by a tight fit. At this time, a radial clearance of the inner race is formed between the free end 13 of the inner race 10 and the axially extending portion (i.e., root portion) 21 of the outer race 20δ₁. The radial extension 22 of the outer retainer 20 extends outward to form a free end 23 thereof, and forms a radial clearance delta of the outer retainer with the inner surface of the bearing outer ring 2₂. Radial clearance delta of the inner retainer ring₁Radial clearance delta of outer retainer ring₂And axial clearance delta between inner and outer retaining rings₃Formed in series as a labyrinth clearance passage, possesses a much better sealing effect than the single-layer retainer ring 5 shown in fig. 1.

The shielding effect of the labyrinth gap channel is directly related to the degree and length of the narrowness of the channel. For the radial clearance delta₁And delta₂In other words, the present invention is designed to use a gap width of 0.2-0.4 mm. Although a narrower clearance is beneficial to further improve the protection effect, the bearing is easy to cause the inner retainer ring and the outer retainer ring to touch opposite parts (detailed later) when the bearing is not in centering operation, so that the friction torque occurs, and even the related retainer rings are accidentally separated. For axial clearance delta₃In other words, the present invention is designed to use a gap width of 0.2-0.8 mm. This is because the axial gap δ₃The mutual interference between the inner retaining ring and the outer retaining ring is easily caused when the bearing is too narrow, and the limited space in the bearing is excessively occupied when the bearing is too wide.

In the embodiment shown in fig. 3, the radial clearance δ of the inner retainer ring 10₁Formed between its free end 13 and an axially extending portion (root portion) 21 of the outer collar 20. However, in the case where the axial extension 21 of the outer retainer 20 is of limited length, or where the outer retainer 20 is employed with a root 11 similar to the inner retainer 10, the radial clearance δ of the inner retainer 10 is₁Or between the free end 13 and the bearing inner ring 1 (not shown). In the latter case, the free end 13 of the inner collar 10 faces radially the bearing inner ring 1, but not the axial extension 21 of the outer collar 20. In a broad sense, the radial clearance delta₁Should be formed by the free end 13 of the inner collar 10 and the part situated diametrically opposite it. The opposite component may be the inner ring 1 of the bearing, or a sealing component located on the inner ring 1 of the bearing, including but not limited to the outer retainer ring 20 and its radial extension (root) 21, or any other type of bearing component. In other words, whether or not the outer retainer ring 20 is formed as shown in FIG. 3The axially extending portions 21 shown in (a) do not prevent the inner race 10 from forming a radial gap δ of the inner race with its radially facing components₁。

Alternatively, as shown in fig. 3, the free end 13 of the inner retainer 10 is formed to have a bent portion 13a turned inward in the axial direction, and the bent portion 13a extends a predetermined length in the axial direction such that the radial gap δ₁Formed as a clearance passage having a certain length in the axial direction. It will be understood that the clearance passage delta has an axial length₁The total length of the labyrinth clearance channel can be lengthened to a certain extent, so that the sealing effect is favorably enhanced, and foreign matters are prevented from entering and grease is prevented from leaking.

Fig. 4 shows a variant embodiment of the invention. In this embodiment, the inner retainer ring 10 is also formed with an axially extending portion 11 extending in the axial direction and a radially extending portion 12 extending in the radial direction, similarly to the case of the outer retainer ring 20. Wherein, the axial extension part 11 is used as the root of the inner retaining ring 10, and the inner retaining ring 10 is fixed on the outer ring 2 of the bearing through tight fit; the radial extension 12 extends radially towards the bearing inner ring 1 to form a radial free end 13 of the inner race 10 and forms a radial gap (delta) of the inner race with a base 21 of the outer race 20 located radially opposite thereto₁). Further, unlike the form of the full-curled root 11 shown in fig. 3, the root 11 (i.e., the axially extending portion) of the inner retainer ring 10 shown in fig. 4 is formed to be vertically turned to the axially outer side and fixed to the outer ring 2 of the bearing by tight fitting, thereby achieving a convenient object of installation without providing the mounting groove 24 for fitting the inner retainer ring 10 on the outer ring 2 of the bearing, but by pushing the inner retainer ring 10 to the shoulder 25 formed on the outer ring 2 of the bearing.

In the embodiment shown in fig. 4, the radial clearance δ of the outer ring 20₂Formed by its free end 23 and the axially extending portion 11 of the inner collar 10. Consider the situation shown in FIG. 3 (radial gap δ)₂Formed by the free end 23 of the outer cage 20 and the bearing outer ring 2), a radial gap δ₂In a broad sense, it should be formed by the axially free end 23 of the outer collar 20 and the part situated diametrically opposite it. The opposite partThe member includes, but is not limited to, the outer race 2 of the bearing, the axial extension 11 of the inner retainer ring 10, or any other type of bearing component.

The non-contact double-layer sealing element is particularly suitable for the deep groove ball bearing with the following radial boundary size: the inner diameter D of the bearing is 15mm, and the outer diameter D is 35 mm; alternatively, the inner diameter D is 17mm and the outer diameter D is 40 mm. The boundary-sized deep groove ball bearings typically include standard deep groove ball bearings of ISO type 6202 and 6203, as well as non-standard designs with adjusted widths in the axial direction. Nevertheless, the invention is generally applicable to other types of rolling bearings where an axial seal is to be installed.

The double-layer structure of the seal requires sufficient space on both sides of the bearing in the axial direction. When the inner space of the bearing is insufficient, it is conceivable to use rolling elements of reduced diameter as an alternative. For example, the diameter D of the rolling elements 3 can be designed_wThe ratio of the bearing diameter D to the inner diameter D of the bearing satisfies the relation D of more than or equal to 20%_wThe/d is less than or equal to 38 percent. The rolling bodies within the above size range allow deep groove ball bearings of 6202 and 6203 type to employ the non-contact double layer seal of the present invention without changing the size of the bearing boundary. Keeping the boundary dimensions constant (at least the radial boundary dimensions) means that the improved bearing can be used directly to replace the original bearing of the device, thus allowing excellent versatility and thus ease of maintenance.

As a preferred embodiment, the diameter D of the rolling elements_wThe ratio of the bearing diameter D to the inner diameter D of the bearing can further satisfy the relation D is more than or equal to 30%_wThe/d is less than or equal to 38 percent. However, the diameter of the rolling element is in positive correlation with the bearing capacity of the bearing, so that excessively reducing the diameter of the rolling element is not favorable for increasing the bearing load of the bearing. In this sense, the diameter D of the rolling elements is further preferred according to the invention_wThe ratio of the bearing diameter D to the inner diameter D of the bearing satisfies the relation D of 34 percent to D_w/d≤38％。

It will be appreciated by those skilled in the art that the above features of the present invention can be implemented independently or in combination without limitation to the specific embodiments. Any variations and modifications of the non-contact double seal and deep groove ball bearing are within the scope of the invention, as long as they are in accordance with the definitions of the appended claims.

Claims

1. A non-contact double-layer sealing element (50) for a rolling bearing comprises an inner retainer ring (10) and an outer retainer ring (20) which are sequentially distributed from inside to outside in the axial direction, and an axial gap (delta) is formed between the two retainer rings (10, 20)₃) Wherein

The inner race (10) is fastened by its base (11) to one of the inner and outer races (1, 2) of the bearing, the radial free end (13) of which forms a radial gap (delta) of the inner race with the radially opposite component (1, 2, 21)₁)；

The outer collar (20) is fastened by its base (21) to the other of the inner and outer rings (1, 2) of the bearing, with its radial free end (23) forming a radial gap (delta) of the outer collar with the radially opposite component (1, 2, 11)₂)。

2. The non-contact bilayer seal (50) of claim 1 wherein: the outer collar (20) is formed with an axially extending portion (21) extending substantially axially inwardly and a radially extending portion (22) extending substantially radially, wherein

The axial extension (21) is used as a base (21) of the outer retainer ring (20) and forms a radial clearance (delta) of the inner retainer ring with the radial free end (13) of the inner retainer ring (10)₁)；

The radial extension part (22) extends to form a radial free end (23) of the outer retainer ring (20), and a radial clearance (delta) of the outer retainer ring is formed between the radial free end and the inner ring (1) or the outer ring (2) of the bearing which is positioned opposite to the radial free end in a radial direction₂)。

3. The non-contact bilayer seal (50) of claim 1 wherein: the inner retainer ring (10) is formed with an axially extending portion (11) extending substantially axially outwardly and a radially extending portion (12) extending substantially radially, wherein

Said axial extension (11) acting as an inner collar(s) ((10) And a radial clearance (delta) of the outer collar (20) is formed between the base (11) of (d) and the radial free end (23) of the outer collar₂)；

The radial extension part (12) extends to form a radial free end (3) of the inner retainer ring (10), and a radial clearance (delta) of the inner retainer ring is formed between the radial free end and a base part (21) of the outer retainer ring (20) which is positioned opposite to the radial free end in the radial direction₁)。

4. The non-contact bilayer seal (50) of claim 1 wherein: the radial free end (13) of the inner retainer ring (10) is turned to the axial inner side, and the radial clearance (delta) of the inner retainer ring corresponding to the turning part (13a)₁) Extending in the axial direction by a predetermined length.

5. The non-contact bilayer seal (50) of claim 1 wherein: radial clearance (delta) of the inner retainer ring₁) Radial clearance (delta) with outer collar₂) In the range of 0.2-0.4 mm, the axial gap (delta) between the inner and outer rings (10, 20)₃) The size range of (a) is between 0.2 and 0.8 mm.

6. The non-contact bilayer seal (50) of claim 1 wherein: the inner retainer ring (10) is arranged on an outer ring (2) of the bearing, and the outer retainer ring (20) is arranged on an inner ring (1) of the bearing.

7. A deep groove ball bearing (100) comprising an inner ring (1), an outer ring (2) and a plurality of rolling elements (3) disposed between the inner and outer rings (1, 2), the bearing (100) having radial boundary dimensions of an inner diameter D of 15mm and an outer diameter D of 35mm, or an inner diameter D of 17mm and an outer diameter D of 40mm, characterized in that: the bearing (100) employs a non-contact double seal (50) according to any one of claims 1 to 5.

8. The deep groove ball bearing (100) as claimed in claim 7, characterized in that: diameter D of the rolling body (3)_wThe ratio of the bearing diameter D to the inner diameter D of the bearing satisfies the relation D of more than or equal to 20%_w/d≤38％。

9. The deep groove ball bearing (100) as claimed in claim 8, characterized in that: diameter D of the rolling body (3)_wThe ratio of the bearing diameter D to the inner diameter D of the bearing further satisfies the relation D is more than or equal to 30%_w/d≤38％。

10. The deep groove ball bearing (100) as claimed in claim 9, characterized in that: diameter D of the rolling body (3)_wThe ratio of the bearing diameter D to the inner diameter D of the bearing further satisfies the relation of 34% to D_w/d≤38％。