WO2016000472A1 - 迷宫式密封轴承 - Google Patents

迷宫式密封轴承 Download PDF

Info

Publication number
WO2016000472A1
WO2016000472A1 PCT/CN2015/075836 CN2015075836W WO2016000472A1 WO 2016000472 A1 WO2016000472 A1 WO 2016000472A1 CN 2015075836 W CN2015075836 W CN 2015075836W WO 2016000472 A1 WO2016000472 A1 WO 2016000472A1
Authority
WO
WIPO (PCT)
Prior art keywords
seal
labyrinth
ring
bearing
extension
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2015/075836
Other languages
English (en)
French (fr)
Inventor
魏来
刘彩芬
刘鑫
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Priority to DE112015003085.9T priority Critical patent/DE112015003085T5/de
Priority to US15/319,846 priority patent/US9926981B2/en
Publication of WO2016000472A1 publication Critical patent/WO2016000472A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Images

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
    • F16C33/80—Labyrinth sealings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/164—Sealings between relatively-moving surfaces the sealing action depending on movements; pressure difference, temperature or presence of leaking fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/40—Sealings between relatively-moving surfaces by means of fluid
    • F16J15/42—Sealings between relatively-moving surfaces by means of fluid kept in sealing position by centrifugal force
    • 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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6607—Retaining the grease in or near the bearing
    • F16C33/6618—Retaining the grease in or near the bearing in a reservoir in the sealing means
    • 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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6622—Details of supply and/or removal of the grease, e.g. purging grease
    • 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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6633—Grease properties or compositions, e.g. rheological properties
    • 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
    • F16C33/74—Sealings of sliding-contact bearings
    • F16C33/741—Sealings of sliding-contact bearings by means of a fluid
    • F16C33/743—Sealings of sliding-contact bearings by means of a fluid retained in the sealing gap

Definitions

  • the present invention relates to the field of bearing technology, and in particular to a labyrinth sealed bearing.
  • FIG. 1 is a schematic partial cross-sectional structural view of one axial end portion of a conventional labyrinth seal bearing.
  • the bearing includes: an inner ring 1; an outer ring 2; a labyrinth seal structure 3, located inside The radial gap (not labeled) between the ring 1 and the outer ring 2 seals the bearing at the axial end of the bearing.
  • the labyrinth seal structure 3 includes a first seal ring 31 fixedly disposed with the outer ring 2, a gap S1 between the inner circumference and the inner ring 1 in the radial direction, and a second seal ring 32 extending in the axial direction and retained on the inner ring 1 a first axially extending portion 32b of the outer surface, and a first radially extending portion 32a extending from the first axially extending portion 32b in a radially outward direction; a third sealing ring 33, and the first sealing ring 31
  • the fixed arrangement includes a second axially extending portion 33b extending in the axial direction, and a second radially extending portion 33a extending from the one end of the second axially extending portion 33b in the radially inward direction.
  • the first radial extension 32a is located between the first sealing ring 31 and the second radial extension 33a, and there is a gap (not identified) between the first radial extension 32a and the second axial extension 33b, second There is a gap S2 between the radially extending portion 33a and the first axially extending portion 32b.
  • a labyrinth gap passage G is formed between the first seal ring 31, the second seal ring 32, and the third seal ring 33, and a gap S1 between the first seal ring 31 and the inner ring 1 and a second radial extension portion 33a and the first
  • the gap S2 between the axially extending portions 32b constitutes both end openings of the labyrinth gap passage G, and the two end portions are open to communicate.
  • One of the end openings communicates with the interior of the bearing and the other end opens into communication with the outside of the bearing.
  • the inside of the bearing refers to the space enclosed by the inner ring 1, the outer ring 2, and the labyrinth seal structure 3.
  • the outer part of the bearing refers to the bearing external environment.
  • the criteria for evaluating the effectiveness of bearing seals are: the ability to prevent external contaminants from entering the bearing and to prevent lubricant leakage within the bearing.
  • the existing labyrinth seal bearing realizes a non-contact seal, and there is a problem that the sealing effect is not good.
  • the problem to be solved by the present invention is that the existing labyrinth seal bearing has a problem of poor sealing effect.
  • the present invention provides a labyrinth seal bearing comprising: an inner ring; an outer ring; a labyrinth seal structure located in a radial gap between the inner ring and the outer ring; the labyrinth seal
  • the structure includes a plurality of sealing rings, and the plurality of sealing rings form a labyrinth gap passage, the labyrinth gap channel has two end openings respectively communicating with the outside of the bearing and the inside of the bearing; the sealing ring formed by the grease is located at the The labyrinth gap channel is closed and the labyrinth gap channel is blocked to isolate the two end openings from each other.
  • the sealing ring is provided with a grease injection through hole for injecting the grease;
  • the labyrinth seal bearing further includes: a sealing cover covering the grease injection through hole.
  • the grease has a taper of 160 or less and a unit of 0.1 mm.
  • the plurality of sealing rings include: a first sealing ring fixedly disposed with the outer ring, including a first radial extending portion extending in a radial direction, the first radial extending portion and the inner portion a first gap exists in the ring;
  • the second seal ring includes a second axial extension extending in the axial direction and being retained on the outer surface of the inner ring, and an end extending from the second axial extension extending in a radially outward direction a second radial extension;
  • the second radial extension being located at the first radial extension and the third Between the radial extensions, there is a second gap between the second radial extension and the third
  • the first sealing ring further includes: a first axial extension extending from an inner circumference of the first radial extension along an axial direction of the bearing gradually away from the second sealing ring, The first axial extension has a gap with the inner ring in the radial direction.
  • the plurality of seal rings further includes: a fourth seal ring including a fourth axial extension extending in the axial direction and holding the outer surface of the second axial extension, and the fourth a fourth radial extension of one end of the axial extension extending in a radially outward direction, a gap between the fourth axial extension and the third radial extension, the fourth radial extension a portion of the third radial extension facing away from the second radial extension; a fifth sealing ring located in the gap between the outer ring and the third axial extension, and fixed On the third axial extension, the fifth seal ring is located radially outward of the fourth radially extending portion and forms a centrifugal seal with the outer periphery of the fourth radially extending portion.
  • the fourth radial extension is provided with a bent portion, and the bent portion is bent at an acute angle by a radially outer end of the fourth radially extending portion in an axially outward direction of the bearing.
  • the radial gap between the fifth seal ring and the bent portion gradually decreases from the axially outward direction of the bearing.
  • the fourth radial extension has a flow guiding side on a side of the bent portion facing away from the fifth sealing ring, between the guiding flow side and the fourth sealing ring axis
  • the angle is an acute angle.
  • the two end openings of the labyrinth gap passage are isolated from each other by the action of the seal ring, even if the external contaminant has an end opening communicating with the outside of the bearing from the labyrinth gap passage, the lubrication in the bearing is entered into the labyrinth gap passage.
  • the agent has an end opening communicating with the inside of the bearing from the labyrinth gap passage into the labyrinth gap passage, and the sealing ring can also prevent external pollutants and lubricant from continuing to advance in the labyrinth gap passage, thereby preventing external pollutants from entering the bearing. And to prevent leakage of lubricant in the bearing, thereby improving the sealing effect of the labyrinth sealed bearing.
  • FIG. 1 is a schematic axial sectional view showing one axial end portion of a conventional labyrinth seal bearing
  • Figure 2 is a schematic partial cross-sectional structural view showing one axial end portion of the labyrinth seal bearing in the first embodiment of the present invention
  • Figure 3 is a schematic partial cross-sectional structural view showing an axial end portion of a labyrinth seal bearing in a second embodiment of the present invention
  • Figure 4 is a schematic partial cross-sectional structural view showing one axial end portion of a labyrinth seal bearing in a third embodiment of the present invention.
  • the labyrinth seal bearing of the present embodiment includes: an inner ring 10; an outer ring 20; a labyrinth seal structure 30 located in a radial gap (not labeled) between the inner ring 10 and the outer ring 20, The inner ring 10 and the outer ring 20 are coaxially sleeved, and the bearing is sealed at the axial end of the bearing.
  • the labyrinth seal structure 30 includes three seal rings, which are a first seal ring 31, a second seal ring 32, and a third seal ring 33, respectively. among them:
  • the first seal ring 31 is fixedly disposed with the outer ring 20 and includes a first radial extension 310 extending in a radial direction.
  • the first radial extension 310 and the inner ring 10 have a first gap S1.
  • the second seal ring 32 includes a second axial extension 321 extending in the axial direction and being retained on the outer surface of the inner ring 10, and a second radial direction extending from the end of the second axial extension 321 in the radially outward direction.
  • the extension 320 is
  • the third seal ring 33 is fixedly disposed with the first seal ring 31 and includes a third axial extension 332 extending in the axial direction, and an end from the third axial extension 332 radially inward. To the extended third radial extension 330, the third axial extension 332 and the outer ring 20 have a gap in the radial direction.
  • the second radial extension 320 is located between the first radial extension 310 and the third radial extension 330, and there is a second gap between the second radial extension 320 and the third axial extension 332 (not identified) There is a third gap S2 between the third radial extension 330 and the second axial extension 321 .
  • the first gap S1, the second gap, and the third gap S2 are sequentially arranged in a direction A from the axial direction of the bearing. That is, in the axial direction of the bearing, the third gap S2 is closest to the external environment, and the first gap S1 is farthest from the external environment.
  • a labyrinth gap passage G is formed between the first seal ring 31, the second seal ring 32, and the third seal ring 33, and the first gap S1 between the first radial extension portion 310 and the inner ring 10 is used as the labyrinth gap passage G.
  • the third seal ring 33 is fixed to the outer ring 20 by being fixed to the first seal ring 31.
  • the third seal ring 33 may be directly fixed to the outer ring 20.
  • the labyrinth seal bearing further includes a seal ring 40 located in the labyrinth gap passage G and blocking the labyrinth gap passage G to isolate the two end openings of the labyrinth gap passage G from each other.
  • the seal ring 40 blocks the labyrinth gap channel G and isolates the two end openings from each other, the seal ring 40 needs to form a contact seal with at least three seal rings.
  • the seal ring 40 forms a contact seal with the first seal ring 31, the second seal ring 32, and the third seal ring 33.
  • the longitudinal section of the seal ring 40 is L-shaped, that is, when the seal ring 40 is cut along the axial direction of the seal ring 40, the cross section of the seal ring 40 is L-shaped.
  • the radially inner end of the seal ring 40 is sandwiched between the second radially extending portion 320 and the third radially extending portion 330 and radially between the second axially extending portion 321 of the second seal ring 32 Gap
  • the axial gap between the second radial extension 320 and the third radial extension 330 is not filled by the seal ring 40.
  • the radially outer end of the seal ring 40 is sandwiched between the second radially extending portion 320 of the second seal ring 32 and the third axial extension 332 of the third seal ring 33, and is in the axial direction of the bearing The two ends abut against the third radial extension 330 of the first seal ring 31 and the third seal ring 33, respectively.
  • the two end openings of the labyrinth gap passage G are isolated from each other by the action of the seal ring 40, even if external contaminants have an end opening communicating with the outside of the bearing from the labyrinth gap passage G into the labyrinth gap passage G, And the lubricant in the bearing has an end opening communicating with the inside of the bearing from the labyrinth gap passage G into the labyrinth gap passage G, and the sealing ring 40 can also prevent external pollutants and the lubricant from continuing to advance in the labyrinth gap passage G. In addition, it can prevent external pollutants from entering the bearing and prevent leakage of lubricant in the bearing, thereby improving the sealing effect of the labyrinth sealed bearing.
  • the lubricant used in the labyrinth seal bearing is a grease.
  • first seal ring 31, the second seal ring 32, and the third seal ring 33 in the labyrinth seal structure 30 are not limited to the embodiment, as long as the first seal ring 31 and the second seal ring are ensured. 32.
  • the third seal ring 33 can form a labyrinth gap passage G to realize a labyrinth seal to the bearing.
  • the number of the seal rings in the labyrinth seal structure 30 is not limited to three, as long as a plurality of seal rings can be formed to form a labyrinth gap passage to realize a labyrinth seal for the bearings.
  • the seal ring 40 is formed of grease, and the third axial extension portion 332 of the third seal ring 33 is provided with a grease injection through hole 331 for injecting grease for forming the seal ring 40.
  • the grease injection through hole 331 is aligned with the axial gap between the second radial extension 320 and the third radial extension 330.
  • the labyrinth seal bearing further includes a sealing cover (not shown) that is attached to the grease injection through hole 331.
  • the method of forming the seal ring 40 using grease is as follows: The sealing cover on the grease injection through hole 331 is removed, and grease is injected from the grease injection through hole 331 into the labyrinth gap passage G; after the grease is injected, the sealing cover is closed in the grease injection through hole 331 Then, the labyrinth seal bearing is rotated, and under the action of the centrifugal force, the grease in the labyrinth gap passage G is scooped out in the radial outward direction of the bearing, and adheres to the first seal ring 31 and the second seal ring 32.
  • the contact ring is formed between the seal ring 40 and the seal ring in the labyrinth seal structure 30 (ie, the first seal ring 31, the second seal ring 32, and the third seal ring 33), due to the seal ring 40
  • the material is grease, so that the friction generated between the sealing ring 40 and the sealing ring is small, so that the bearing does not generate a large amount of heat during operation, and does not cause serious wear on the labyrinth sealing structure 30, thereby enabling Extend the service life of the bearing.
  • the seal 40 may be lost due to the friction between the seal ring in the labyrinth seal structure 30 and the partial grease in the seal ring 40 being pulled out due to the centrifugal force. Refill the labyrinth gap channel G with grease. In this way, when the bearing is in operation, the re-injected grease is pulled out in the radially outward direction under the centrifugal force to compensate the loss portion in the sealing ring 40, so that the sealing ring 40 can always be the same
  • a seal ring 31, a second seal ring 32, and a third seal ring 33 form a contact seal to ensure that the bearing always has a good sealing effect.
  • the labyrinth gap is injected.
  • the amount of grease in channel G should not be too small. The specific amount of injection required for the grease can be determined by experimentation.
  • the sealing ring 40 in order to prevent the more grease in the sealing ring 40 from being pulled out under the centrifugal force during the operation of the bearing, the sealing ring 40 cannot continue with the first sealing ring 31 and the second sealing ring 32,
  • the third seal ring 33 forms a contact seal, and the grease used to form the seal ring 40 has a greater consistency and is thicker than the seal used as a lubricant in the bearing.
  • a grease having a consistency level of five or more can be used to form the seal ring 40 of the present embodiment.
  • the grease with a consistency grade of five has a cone penetration of 130 to 160 (unit: 0.1 mm)
  • the grease of a consistency grade of six has a cone penetration of 85 to 115 (unit: 0.1 mm).
  • the first seal ring 31 further includes: a first axial extension 311 extending from the first radial direction The inner circumference of the portion 310 extends along the axial direction of the bearing away from the second seal ring 32, and the first axial extension portion 311 and the inner ring 10 have a gap (not labeled) in the radial direction; the labyrinth seal structure further includes a fourth seal Ring 34 and fifth seal ring 35.
  • the bearing When the bearing is in operation, it is possible for the lubricant in the bearing to be sputtered onto the side surface 312 of the first seal ring 31 facing away from the second seal ring 32.
  • the bearing is radially located in the upper half of the bearing axis (shown in the drawing), and the lubricant on the side surface 312 flows in the radial inward direction of the bearing to the first shaft under the action of its own gravity.
  • the lubricant On the outer circumferential surface of the extending portion 311, the lubricant does not easily flow into the first gap S1, so that the lubricant in the bearing does not easily leak.
  • the first axial extension 311 can extend the leakage path of the lubricant, allowing the lubricant to flow through the first axial direction.
  • the labyrinth gap passage G can be entered, so that the lubricant in the bearing is not easily leaked.
  • the fourth seal ring 34 includes a fourth axial extension 342 extending in the axial direction and being retained on the outer surface of the second axial extension 321 , and an end extending from the fourth axial extension 342 in the radially outward direction
  • the fourth radial extension 341 has a gap between the fourth axial extension 342 and the third radial extension 330, and the fourth radial extension 341 is located at the third radial extension 330 away from the second radial extension.
  • One side of the portion 320 is one side of the portion 320.
  • the fifth seal ring 35 is located in the gap between the outer ring 20 and the third axial extension 332 and is fixed on the third axial extension 332.
  • the fifth seal ring 35 is located at the fourth radial extension 341. Radially outside, and the outer circumference of the fifth seal ring 35 and the fourth radially extending portion 341 has a gap S3 in the radial direction, and forms a centrifugal seal.
  • a through hole (not labeled) is disposed at a position corresponding to the grease injection through hole 331 in the fifth seal ring 35 to inject grease into the labyrinth gap passage G through the through hole and the grease injection through hole 331.
  • a seal ring 40 is formed.
  • the leakage path of the lubricant in the bearing and the path of external contaminants entering the bearing can be prolonged, thereby further improving the sealing effect of the bearing.
  • the fourth radially extending portion 341 is provided with a bent portion 3412, and the bent portion 3412 is formed by the radially outer end of the fourth radially extending portion 341 in the axial direction outward of the bearing A (ie, from the first The axial direction of the three radial extending portions 330 to the fourth radially extending portion 341 is bent at an acute angle. From the axially outward direction A of the bearing, the fifth seal ring 35 and the bent portion 3412 The radial gap S3 is gradually reduced.
  • the direction A of the radial gap S3 from the axial direction of the bearing is a convergence gap, so that the external pollutant entering the space between the fourth radial extension 341 and the third radial extension 330 is more likely to be in the centrifugal force. Under the action of the radial gap S3 is pulled out to obtain a better sealing effect.
  • the fourth radially extending portion 341 has an outer side surface 3410 facing away from the third sealing ring 33 in the axial direction of the bearing, and a flow guiding side 3411 located at the bent portion 3412 facing away from the fifth sealing ring.
  • the angle between the flow guiding side 3411 and the axis of the fourth sealing ring 34 is an acute angle such that the vertical distance between the guiding side 3411 and the axis of the fourth sealing ring 34 gradually increases from the axially outward direction A of the bearing.
  • the longitudinal section of the seal ring 40 is in a straight shape, that is, the seal is cut along the axial direction of the seal ring 40.
  • the cross section of the sealing ring 40 is in a straight shape, and the sealing ring 40 is sandwiched between the second radially extending portion 320 of the second sealing ring 32 and the third axial extending portion 332 of the third sealing ring 33.
  • its two ends in the axial direction of the bearing abut against the third radial extension 330 of the first seal ring 31 and the third seal ring 33, respectively.
  • the position of the grease injection through hole is selected according to the position of the sealing ring in the labyrinth gap channel to form a sealing ring at a specified position in the labyrinth gap channel.
  • the shape of the sealing ring and the gap in the labyrinth should not be limited to the above-described embodiments, and other variations are possible.
  • the embodiments use a progressive writing method, and the differences from the foregoing embodiments are mainly described.
  • the same portions in the respective embodiments can be referred to the foregoing embodiments.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing Of Bearings (AREA)

Abstract

一种迷宫式密封轴承，包括：内圈（10）；外圈（20）；迷宫式密封结构（30），其位于该内圈（10）与外圈（20）之间的径向间隙内；该迷宫式密封结构（30）包括多个密封环，该多个密封环之间形成迷宫间隙通道（G），该迷宫间隙通道（G）具有两个分别连通轴承外部、轴承内部的端部开口；由润滑脂形成的密封圈（40），位于迷宫间隙通道（G）内，并将迷宫间隙通道（G）阻塞，使两个端部开口彼此隔绝，其解决了现有迷宫式密封轴承存在密封效果不佳的问题。

Description

迷宫式密封轴承
本申请要求2014年7月2日提交中国专利局、申请号为201410313655.4、发明名称为“迷宫式密封轴承”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本发明涉及轴承技术领域，特别是涉及一种迷宫式密封轴承。
背景技术
图1是现有一种迷宫式密封轴承其中一个轴向端部的轴向局部剖面结构示意图，如图1所示，该轴承包括：内圈1；外圈2；迷宫式密封结构3，位于内圈1与外圈2之间的径向间隙(未标识)内，并在轴承的轴向端部密封轴承。
迷宫式密封结构3包括：第一密封环31，与外圈2固定设置，内周缘与内圈1沿径向存在间隙S1；第二密封环32，包括沿轴向延伸并固持于内圈1外表面的第一轴向延伸部32b、及自第一轴向延伸部32b的一端沿径向向外方向延伸的第一径向延伸部32a；第三密封环33，与第一密封环31固定设置，包括沿轴向延伸的第二轴向延伸部33b、及自第二轴向延伸部33b的一端沿径向向内方向延伸的第二径向延伸部33a。第一径向延伸部32a位于第一密封环31与第二径向延伸部33a之间，第一径向延伸部32a与第二轴向延伸部33b之间存在间隙(未标识)，第二径向延伸部33a与第一轴向延伸部32b之间存在间隙S2。
第一密封环31、第二密封环32、第三密封环33之间形成迷宫间隙通道G，第一密封环31与内圈1之间的间隙S1、第二径向延伸部33a与第一轴向延伸部32b之间的间隙S2构成迷宫间隙通道G的两个端部开口，且所述两个端部开口连通。其中一个端部开口与轴承内部连通、另一端部开口与轴承外部连通。轴承内部是指由内圈1、外圈2、以及迷宫式密封结构3围成的空间，轴承外部是指轴承所处的 外界环境。
评价轴承密封效果好坏的标准是：防止外界污染物进入轴承、以及防止轴承内的润滑剂泄露的能力。但是，现有迷宫式密封轴承实现的是非接触式密封，存在密封效果不佳的问题。
发明内容
本发明要解决的问题是：现有迷宫式密封轴承存在密封效果不佳的问题。
为解决上述问题，本发明提供了一种迷宫式密封轴承，包括：内圈；外圈；迷宫式密封结构，位于所述内圈与外圈之间的径向间隙内；所述迷宫式密封结构包括多个密封环，所述多个密封环之间形成迷宫间隙通道，所述迷宫间隙通道具有两个分别连通轴承外部、轴承内部的端部开口；由润滑脂形成的密封圈，位于所述迷宫间隙通道内，并将所述迷宫间隙通道阻塞，使两个所述端部开口彼此隔绝。
可选的，所述密封环设有注脂通孔，用于所述润滑脂的注入；所述迷宫式密封轴承还包括：密封盖，盖合在所述注脂通孔上。
可选的，所述润滑脂的锥入度小于等于160，单位为0.1mm。
可选的，所述多个密封环包括：第一密封环，与所述外圈固定设置，包括沿径向延伸的第一径向延伸部，所述第一径向延伸部与所述内圈存在第一间隙；第二密封环，包括沿轴向延伸并固持于内圈外表面的第二轴向延伸部、及自所述第二轴向延伸部的一端沿径向向外方向延伸的第二径向延伸部；第三密封环，与所述外圈固定设置，包括沿轴向延伸的第三轴向延伸部、及自所述第三轴向延伸部的一端沿径向向内方向延伸的第三径向延伸部，所述第三轴向延伸部与外圈沿径向存在间隙；所述第二径向延伸部位于所述第一径向延伸部和所述第三径向延伸部之间，所述第二径向延伸部与第三轴向延伸部之间存在第二间隙，所述第三径向延伸部与第二轴向延伸部之间存在第三间隙；所述第一、二、三间隙自轴承轴向向外的方向依次间隔排列，所 述第一间隙和第三间隙作为所述迷宫间隙通道的两个端部开口。
可选的，所述第一密封环还包括：第一轴向延伸部，自所述第一径向延伸部的内周缘沿轴承逐渐远离所述第二密封环的轴向方向延伸，所述第一轴向延伸部与内圈沿径向存在间隙。
可选的，所述多个密封环还包括：第四密封环，包括沿轴向延伸并固持于所述第二轴向延伸部外表面的第四轴向延伸部、及自所述第四轴向延伸部的一端沿径向向外方向延伸的第四径向延伸部，所述第四轴向延伸部与所述第三径向延伸部之间存在间隙，所述第四径向延伸部位于所述第三径向延伸部背向所述第二径向延伸部的一侧；第五密封环，位于所述外圈与第三轴向延伸部之间的间隙内，并固设于所述第三轴向延伸部上，所述第五密封环位于第四径向延伸部的径向外侧，并与所述第四径向延伸部的外周缘形成离心式密封。
可选的，所述第四径向延伸部设有弯折部，所述弯折部由所述第四径向延伸部的径向外端沿轴承轴向向外的方向弯折一锐角而成；自轴承轴向向外的方向，所述第五密封环与所述弯折部之间的径向间隙逐渐减小。
可选的，所述第四径向延伸部具有：导流侧面，位于所述弯折部背向所述第五密封环的一侧，所述导流侧面与第四密封环轴线之间的夹角为锐角。
与现有技术相比，本发明的技术方案具有以下优点：
由于在密封圈的作用下，迷宫间隙通道的两个端部开口彼此隔绝，因此，即使外界污染物有从迷宫间隙通道中与轴承外部连通的端部开口进入迷宫间隙通道内、轴承内的润滑剂有从迷宫间隙通道中与轴承内部连通的端部开口进入迷宫间隙通道内，密封圈也能阻止外界污染物、以及润滑剂在迷宫间隙通道内继续前进，进而能够防止外界污染物进入轴承内、以及防止轴承内的润滑剂泄漏，从而提高了迷宫式密封轴承的密封效果。
附图说明
图1是现有一种迷宫式密封轴承其中一个轴向端部的轴向局部剖面结构示意图；
图2是本发明的第一实施例中迷宫式密封轴承其中一个轴向端部的轴向局部剖面结构示意图；
图3是本发明的第二实施例中迷宫式密封轴承其中一个轴向端部的轴向局部剖面结构示意图；
图4是本发明的第三实施例中迷宫式密封轴承其中一个轴向端部的轴向局部剖面结构示意图。
具体实施方式
为使本发明的上述目的、特征和优点能够更为明显易懂，下面结合附图对本发明的具体实施例做详细的说明。
第一实施例
如图2所示，本实施例的迷宫式密封轴承包括：内圈10；外圈20；迷宫式密封结构30，位于内圈10与外圈20之间的径向间隙(未标识)内，与内圈10、外圈20同轴套设，并在轴承的轴向端部密封轴承。迷宫式密封结构30包括三个密封环，分别为第一密封环31、第二密封环32、第三密封环33。其中：
第一密封环31与外圈20固定设置，并包括沿径向延伸的第一径向延伸部310，第一径向延伸部310与内圈10存在第一间隙S1。
第二密封环32包括沿轴向延伸并固持于内圈10外表面的第二轴向延伸部321、及自第二轴向延伸部321的一端沿径向向外方向延伸的第二径向延伸部320。
第三密封环33与第一密封环31固定设置，并包括沿轴向延伸的第三轴向延伸部332、及自第三轴向延伸部332的一端沿径向向内方 向延伸的第三径向延伸部330，第三轴向延伸部332与外圈20沿径向存在间隙。
第二径向延伸部320位于第一径向延伸部310和第三径向延伸部330之间，第二径向延伸部320与第三轴向延伸部332之间存在第二间隙(未标识)，第三径向延伸部330与第二轴向延伸部321之间存在第三间隙S2。
第一间隙S1、所述第二间隙、第三间隙S2自轴承轴向向外的方向A依次间隔排列。即，在轴承轴向方向上，第三间隙S2最靠近外界环境，第一间隙S1最远离外界环境。
第一密封环31、第二密封环32、第三密封环33之间形成迷宫间隙通道G，且第一径向延伸部310与内圈10之间的第一间隙S1作为迷宫间隙通道G中与轴承内部连通的端部开口，第三径向延伸部330与第二轴向延伸部321之间的第三间隙S3作为迷宫间隙通道G中与轴承外部连通的端部开口。
在本实施例中，第三密封环33通过固定在第一密封环31上从而实现与外圈20固定设置。在本实施例的变换例中，第三密封环33也可以直接固定在外圈20上。
所述迷宫式密封轴承还包括：密封圈40，位于迷宫间隙通道G内，并将迷宫间隙通道G阻塞，使迷宫间隙通道G的两个端部开口彼此隔绝。为了实现密封圈40将迷宫间隙通道G阻塞，且使两个端部开口彼此隔绝，密封圈40需与至少三个密封环形成接触式密封。在本实施例中，密封圈40与第一密封环31、第二密封环32、第三密封环33均形成接触式密封。
在本实施例中，密封圈40的纵截面呈L型，即沿着密封圈40的轴线方向切割密封圈40时，密封圈40的截面呈L型。密封圈40的径向内端夹持在第二径向延伸部320与第三径向延伸部330之间，并与第二密封环32的第二轴向延伸部321之间沿径向存在间隙，使 得第二径向延伸部320与第三径向延伸部330之间的轴向间隙未被密封圈40填满。密封圈40的径向外端夹持在第二密封环32的第二径向延伸部320与第三密封环33的第三轴向延伸部332之间，且其在轴承轴向方向上的两端分别抵靠第一密封环31、第三密封环33的第三径向延伸部330。
由于在密封圈40的作用下，迷宫间隙通道G的两个端部开口彼此隔绝，因此，即使外界污染物有从迷宫间隙通道G中与轴承外部连通的端部开口进入迷宫间隙通道G内、以及轴承内的润滑剂有从迷宫间隙通道G中与轴承内部连通的端部开口进入迷宫间隙通道G内，密封圈40也能阻止外界污染物、以及润滑剂在迷宫间隙通道G内继续前进，进而能够防止外界污染物进入轴承内、以及防止轴承内的润滑剂泄漏，从而提高了迷宫式密封轴承的密封效果。
在本实施例中，迷宫式密封轴承所采用的润滑剂为润滑脂。
需说明的是，迷宫式密封结构30中第一密封环31、第二密封环32、第三密封环33的形状并不能局限于本实施例，只要保证第一密封环31、第二密封环32、第三密封环33能够形成迷宫间隙通道G以对轴承实现迷宫式密封即可。
另外，在本发明的技术方案中，迷宫式密封结构30中密封环的数量并不应局限于三个，只要保证多个密封环能够形成迷宫间隙通道以对轴承实现迷宫式密封即可。
密封圈40由润滑脂形成，第三密封环33的第三轴向延伸部332设有注脂通孔331，用于注入用来形成密封圈40的润滑脂。注脂通孔331对准第二径向延伸部320和第三径向延伸部330之间的轴向间隙。
所述迷宫式密封轴承还包括：密封盖(未图示)，盖合在注脂通孔331上。
在本实施例中，利用润滑脂形成密封圈40的方法如下：将盖合 在注脂通孔331上的所述密封盖拆卸下来，从注脂通孔331向迷宫间隙通道G内注入润滑脂；润滑脂注入完之后，将所述密封盖盖合在注脂通孔331上，然后转动迷宫式密封轴承，在离心力的作用下，迷宫间隙通道G内的润滑脂会沿轴承径向向外的方向被甩出，并黏附在第一密封环31、第二密封环32、第三密封环33上，随着迷宫式密封轴承转动时间的加长，越来越多的润滑脂会黏附在第一密封环31、第二密封环32、第三密封环33上，直至由润滑脂所形成的密封圈40与第一密封环31、第二密封环32、第三密封环33均形成接触式密封，以将迷宫间隙通道G阻塞。
虽然密封圈40与迷宫式密封结构30中的密封环(即第一密封环31、第二密封环32、第三密封环33)之间形成的是接触式密封，但是，由于密封圈40的材料是润滑脂，使得密封圈40与密封环之间所产生的摩擦较小，因此，轴承工作时不会产生大量的热量，也不会对迷宫式密封结构30造成较为严重的磨损，进而能够延长轴承的使用寿命。
另外，即使轴承使用一段时间之后，密封圈40会因与迷宫式密封结构30中密封环之间的摩擦、以及密封圈40中的部分润滑脂因离心力作用被甩出而有所损耗，也可以向迷宫间隙通道G重新注入润滑脂。这样一来，在轴承工作时，重新注入的润滑脂会在离心力的作用下沿径向向外的方向被甩出以对密封圈40中的损耗部分进行补偿，使得密封圈40能够始终与第一密封环31、第二密封环32、第三密封环33形成接触式密封，保证轴承始终具有良好的密封效果。
而且，即使轴承使用一段时间之后，密封圈40中的部分润滑脂因离心力作用被甩出，被甩出的润滑脂也会与轴承内用作润滑剂的润滑脂融合，不会影响轴承的润滑效果。
需说明的是，为了使由注入迷宫间隙通道G内的润滑脂所形成的密封圈40能够与第一密封环31、第二密封环32、第三密封环33形成接触式密封，注入迷宫间隙通道G内的润滑脂的量不能太少， 润滑脂所需的具体注入量可以通过试验来确定。
另外还需说明的是，为了防止轴承工作时密封圈40中的较多润滑脂会在离心力作用下被甩出，进而导致密封圈40无法继续与第一密封环31、第二密封环32、第三密封环33形成接触式密封，需使用于形成密封圈40的润滑脂的稠度较大一些，其稠度大于轴承内用作润滑剂的润滑脂的稠度。
经大量研究发现，当用于形成密封圈40的润滑脂的锥入度(在本发明中用来表示润滑脂稠度的一种标量)小于等于160(单位为0.1mm)时，能保证密封圈40形成之后在轴承工作时密封圈40中的部分润滑脂不容易在离心力作用下被甩出，使密封圈40能够较长时间的与第二密封环32、第三密封环33形成接触式密封。
在具体实施例中，现有稠度等级为五级或以上的润滑脂能够用来形成本实施例的密封圈40。其中，稠度等级为五级的润滑脂的锥入度为130至160(单位为0.1mm)，稠度等级为六级的润滑脂的锥入度为85至115(单位为0.1mm)。
第二实施例
第二实施例与第一实施例之间的区别在于：在第二实施例中，如图3所示，第一密封环31还包括：第一轴向延伸部311，自第一径向延伸部310的内周缘沿轴承逐渐远离第二密封环32的轴向方向延伸，第一轴向延伸部311与内圈10沿径向存在间隙(未标识)；迷宫式密封结构还包括第四密封环34和第五密封环35。
轴承工作时，轴承内的润滑剂有可能溅射到第一密封环31背向第二密封环32的侧表面312上。这样一来，轴承沿径向位于轴承轴线的上半部分(图中所示)中，侧表面312上的润滑剂会在自身重力的作用下沿轴承径向向内的方向流动至第一轴向延伸部311的外圆周表面上，使润滑剂不容易流到第一间隙S1内，进而使轴承内的润滑剂不容易泄漏。
另外，即使润滑剂有流到第一轴向延伸部311与内圈10之间的间隙内，第一轴向延伸部311也能够延长润滑剂的泄漏路径，使润滑剂流经第一轴向延伸部311与内圈10之间的径向间隙之后才能进入迷宫间隙通道G，进而使轴承内的润滑剂不容易泄漏。
第四密封环34包括沿轴向延伸并固持于第二轴向延伸部321外表面的第四轴向延伸部342、及自第四轴向延伸部342的一端沿径向向外方向延伸的第四径向延伸部341，第四轴向延伸部342与第三径向延伸部330之间存在间隙，第四径向延伸部341位于第三径向延伸部330背向第二径向延伸部320的一侧。
第五密封环35位于外圈20与第三轴向延伸部332之间的间隙内，并固设于第三轴向延伸部332上，第五密封环35位于第四径向延伸部341的径向外侧，且第五密封环35与第四径向延伸部341的外周缘沿径向存在间隙S3，并形成离心式密封。
在本实施例中，第五密封环35中对应注脂通孔331的位置设有通孔(未标识)，以经由该通孔以及注脂通孔331向迷宫间隙通道G内注入润滑脂以形成密封圈40。
通过在迷宫式密封结构30中设置第四密封环34及第五密封环35，可以延长轴承内润滑剂的泄漏路径、以及外界污染物进入轴承内的路径，进而进一步提高轴承的密封效果。
另外，即使外界污染物有从第五密封环35与第四密封环34之间的径向间隙S3进入第三主体部341与第三径向延伸部330之间的间隔内，外界污染物也很容易在离心力的作用下从径向间隙S3被甩出，防止外界污染物进入轴承内。
在本实施例中，第四径向延伸部341设有弯折部3412，弯折部3412由第四径向延伸部341的径向外端沿轴承轴向向外的方向A(即自第三径向延伸部330至第四径向延伸部341的轴向方向)弯折一锐角而成。自轴承轴向向外的方向A，第五密封环35与弯折部3412之 间的径向间隙S3逐渐减小。这样一来，径向间隙S3自轴承轴向向外的方向A为收敛间隙，使得进入第四径向延伸部341与第三径向延伸部330之间间隔内的外界污染物更容易在离心力的作用下从径向间隙S3被甩出，以获得更佳的密封效果。
在本实施例中，第四径向延伸部341具有：外侧面3410，在轴承的轴向方向上背向第三密封环33；导流侧面3411，位于弯折部3412背向第五密封环35的一侧。导流侧面3411与第四密封环34轴线之间的夹角为锐角，使得自轴承轴向向外的方向A，导流侧面3411与第四密封环34轴线之间的垂直距离逐渐增大。
轴承工作时，外界污染物(如污水)有可能溅射到第四径向延伸部341的外侧面3410上。轴承中沿径向位于轴承轴线的下半部分(未图示，图中显示的是轴承沿径向位于轴承轴线的上半部分)中，外侧面3410上的外界污染物会在自身重力的作用下沿轴承径向向外的方向流动至导流侧面3411，使外界污染物离开轴承，进而不容易掉入第五密封环35与第四密封环34之间的径向间隙S3内，进而使外界污染物不容易进入轴承内，以获得更佳的密封效果。
第三实施例
第三实施例与第二实施例之间的区别在于：在第三实施例中，如图4所示，密封圈40的纵截面呈一字型，即沿着密封圈40的轴线方向切割密封圈40时，密封圈40的截面呈一字型，密封圈40夹持在第二密封环32的第二径向延伸部320与第三密封环33的第三轴向延伸部332之间，且其在轴承轴向方向上的两端分别抵靠第一密封环31、第三密封环33的第三径向延伸部330。
需说明的是，当密封圈的材料为润滑脂时，需根据密封圈在迷宫间隙通道内的位置来选择注脂通孔的位置，以在迷宫间隙通道内的指定位置形成密封圈。
另外，在本发明的技术方案中，密封圈的形状、以及在迷宫间隙 通道内的位置并不应仅局限于上述所给实施例，也可以作其他变形。
本发明中，各实施例采用递进式写法，重点描述与前述实施例的不同之处，各实施例中的相同部分可以参照前述实施例。
虽然本发明披露如上，但本发明并非限定于此。任何本领域技术人员，在不脱离本发明的精神和范围内，均可作各种更动与修改，因此本发明的保护范围应当以权利要求所限定的范围为准。

Claims (8)

  1. 一种迷宫式密封轴承，包括：
    内圈；
    外圈；
    迷宫式密封结构，位于所述内圈与外圈之间的径向间隙内；
    所述迷宫式密封结构包括多个密封环，所述多个密封环之间形成迷宫间隙通道，所述迷宫间隙通道具有两个分别连通轴承外部、轴承内部的端部开口；
    其特征在于，还包括：由润滑脂形成的密封圈，位于所述迷宫间隙通道内，并将所述迷宫间隙通道阻塞，使两个所述端部开口彼此隔绝。
  2. 如权利要求1所述的迷宫式密封轴承，其特征在于，所述密封环设有注脂通孔，用于所述润滑脂的注入；
    所述迷宫式密封轴承还包括：密封盖，盖合在所述注脂通孔上。
  3. 如权利要求1所述的迷宫式密封轴承，其特征在于，所述润滑脂的锥入度小于等于160，单位为0.1mm。
  4. 如权利要求1至3任一项所述的迷宫式密封轴承，其特征在于，所述多个密封环包括：
    第一密封环，与所述外圈固定设置，包括沿径向延伸的第一径向延伸部，所述第一径向延伸部与所述内圈存在第一间隙；
    第二密封环，包括沿轴向延伸并固持于内圈外表面的第二轴向延伸部、及自所述第二轴向延伸部的一端沿径向向外方向延伸的第二径 向延伸部；
    第三密封环，与所述外圈固定设置，包括沿轴向延伸的第三轴向延伸部、及自所述第三轴向延伸部的一端沿径向向内方向延伸的第三径向延伸部，所述第三轴向延伸部与外圈沿径向存在间隙；
    所述第二径向延伸部位于所述第一径向延伸部和所述第三径向延伸部之间，所述第二径向延伸部与第三轴向延伸部之间存在第二间隙，所述第三径向延伸部与第二轴向延伸部之间存在第三间隙；
    所述第一、二、三间隙自轴承轴向向外的方向依次间隔排列，所述第一间隙和第三间隙作为所述迷宫间隙通道的两个端部开口。
  5. 如权利要求4所述的迷宫式密封轴承，其特征在于，所述第一密封环还包括：第一轴向延伸部，自所述第一径向延伸部的内周缘沿轴承逐渐远离所述第二密封环的轴向方向延伸，所述第一轴向延伸部与内圈沿径向存在间隙。
  6. 如权利要求4所述的迷宫式密封轴承，其特征在于，所述多个密封环还包括：
    第四密封环，包括沿轴向延伸并固持于所述第二轴向延伸部外表面的第四轴向延伸部、及自所述第四轴向延伸部的一端沿径向向外方向延伸的第四径向延伸部，所述第四轴向延伸部与所述第三径向延伸部之间存在间隙，所述第四径向延伸部位于所述第三径向延伸部背向所述第二径向延伸部的一侧；
    第五密封环，位于所述外圈与第三轴向延伸部之间的间隙内，并固设于所述第三轴向延伸部上，所述第五密封环位于第四径向延伸部 的径向外侧，并与所述第四径向延伸部的外周缘形成离心式密封。
  7. 如权利要求6所述的迷宫式密封轴承，其特征在于，所述第四径向延伸部设有弯折部，所述弯折部由所述第四径向延伸部的径向外端沿轴承轴向向外的方向弯折一锐角而成；
    自轴承轴向向外的方向，所述第五密封环与所述弯折部之间的径向间隙逐渐减小。
  8. 如权利要求7所述的迷宫式密封轴承，其特征在于，所述第四径向延伸部具有：导流侧面，位于所述弯折部背向所述第五密封环的一侧，所述导流侧面与第四密封环轴线之间的夹角为锐角。
PCT/CN2015/075836 2014-07-02 2015-04-03 迷宫式密封轴承 Ceased WO2016000472A1 (zh)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112015003085.9T DE112015003085T5 (de) 2014-07-02 2015-04-03 Wälzlager mit Labyrinthdichtung
US15/319,846 US9926981B2 (en) 2014-07-02 2015-04-03 Labyrinth seal bearing

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201410313655.4 2014-07-02
CN201410313655.4A CN105465187B (zh) 2014-07-02 2014-07-02 迷宫式密封轴承

Publications (1)

Publication Number Publication Date
WO2016000472A1 true WO2016000472A1 (zh) 2016-01-07

Family

ID=55018412

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2015/075836 Ceased WO2016000472A1 (zh) 2014-07-02 2015-04-03 迷宫式密封轴承

Country Status (4)

Country Link
US (1) US9926981B2 (zh)
CN (1) CN105465187B (zh)
DE (1) DE112015003085T5 (zh)
WO (1) WO2016000472A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109261378A (zh) * 2018-11-20 2019-01-25 中国工程物理研究院总体工程研究所 大型高速土工离心机主轴动密封结构

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114934947B (zh) * 2022-06-20 2025-10-17 山西新环精密制造股份有限公司 一种甲片式塑料平面轴承

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4093324A (en) * 1977-05-16 1978-06-06 Emerson Electric Co. Seal for self-aligning bearing
CN202182114U (zh) * 2011-06-22 2012-04-04 栾清杨 一种迷宫式密封轴承
CN203023297U (zh) * 2012-11-20 2013-06-26 北方重工集团有限公司 一种双齿辊破碎机主轴轴承的迷宫密封结构
DE102011089770A1 (de) * 2011-12-23 2013-06-27 Schaeffler Technologies AG & Co. KG Wälzlageranordnung
CN203214651U (zh) * 2013-03-05 2013-09-25 宋建华 一种轴承装置

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4770424A (en) * 1985-12-19 1988-09-13 The Timken Company Compact labyrinth-type seal
CA2215174A1 (en) * 1996-09-11 1998-03-11 David R. Mundy Seal for bearing housing
US6722657B2 (en) * 2002-05-31 2004-04-20 Stemco Llc Low torque seal assembly with open cell filter media
EP1382868A2 (en) * 2002-07-02 2004-01-21 Aktiebolaget SKF Seal arrangement for ball bearing
US6845987B2 (en) * 2002-09-10 2005-01-25 United Technologies Corporation Shaft seal
JP2005140169A (ja) * 2003-11-04 2005-06-02 Ntn Corp 回転センサ付き軸受
JP2007139075A (ja) * 2005-11-18 2007-06-07 Ntn Corp 回転センサ付軸受
US8342535B2 (en) * 2007-11-20 2013-01-01 The Timken Company Non-contact labyrinth seal assembly and method of construction thereof
DE102009009226B4 (de) * 2009-02-17 2011-12-01 Ab Skf Labyrinthdichtung und Verfahren zur Herstellung einer Labyrinthdichtung
CN203246821U (zh) * 2013-04-28 2013-10-23 山西华鑫电气有限公司 超高分子量聚乙烯托辊

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4093324A (en) * 1977-05-16 1978-06-06 Emerson Electric Co. Seal for self-aligning bearing
CN202182114U (zh) * 2011-06-22 2012-04-04 栾清杨 一种迷宫式密封轴承
DE102011089770A1 (de) * 2011-12-23 2013-06-27 Schaeffler Technologies AG & Co. KG Wälzlageranordnung
CN203023297U (zh) * 2012-11-20 2013-06-26 北方重工集团有限公司 一种双齿辊破碎机主轴轴承的迷宫密封结构
CN203214651U (zh) * 2013-03-05 2013-09-25 宋建华 一种轴承装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109261378A (zh) * 2018-11-20 2019-01-25 中国工程物理研究院总体工程研究所 大型高速土工离心机主轴动密封结构
CN109261378B (zh) * 2018-11-20 2023-12-22 中国工程物理研究院总体工程研究所 大型高速土工离心机主轴动密封结构

Also Published As

Publication number Publication date
CN105465187B (zh) 2019-04-12
DE112015003085T5 (de) 2017-03-16
US9926981B2 (en) 2018-03-27
CN105465187A (zh) 2016-04-06
US20170152892A1 (en) 2017-06-01

Similar Documents

Publication Publication Date Title
CN103542004B (zh) 具有密封装置的轮毂轴承组件
CN104912919B (zh) 圆锥滚子轴承
JP6582566B2 (ja) 転がり軸受
CN104421343A (zh) 特别用于滚动轴承的密封和信号装置
RU2585125C2 (ru) Узел подшипника качения
CN102918288A (zh) 具有密封垫片和环形护罩的滚动轴承
CN102422034A (zh) 带有用于防止润滑介质溢出的保持架的滚动轴承
JP6852260B2 (ja) ころ軸受
CN205101403U (zh) 轻薄型圆锥滚子轴承保持架
CN105465188A (zh) 轴承
JP2017133569A (ja) 転がり軸受
TWI632961B (zh) 輥軋機的密封組件及頸密封件
JP2014088891A (ja) 転がり軸受装置
US20100061673A1 (en) Retainer of ball bearing
JP2018066396A (ja) 転がり軸受
CN105465187A (zh) 迷宫式密封轴承
CN105387068B (zh) 用于运载工具的旋转枢轴轴承
US20110193295A1 (en) Sealing arrangement between a stationary first machine part and a second machine part that rotates around the first machine part
CN206175487U (zh) 滚动轴承保持架
JP5146189B2 (ja) 転がり軸受
CN106763781B (zh) 转动机械的液体密封结构
CN205823962U (zh) 一种带中部密封结构的轴承
CN217130334U (zh) 一种卧螺离心机中的轴间密封装置
CN205154917U (zh) 用于轴承的密封结构
CN104948591A (zh) 铁路用密封式圆柱滚子轴承

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 15814387

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 15319846

Country of ref document: US

WWE Wipo information: entry into national phase

Ref document number: 112015003085

Country of ref document: DE

122 Ep: pct application non-entry in european phase

Ref document number: 15814387

Country of ref document: EP

Kind code of ref document: A1