WO2015188640A1 - 轴承 - Google Patents

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Publication number
WO2015188640A1
WO2015188640A1 PCT/CN2015/073920 CN2015073920W WO2015188640A1 WO 2015188640 A1 WO2015188640 A1 WO 2015188640A1 CN 2015073920 W CN2015073920 W CN 2015073920W WO 2015188640 A1 WO2015188640 A1 WO 2015188640A1
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WO
WIPO (PCT)
Prior art keywords
ring
bearing
seal
contact
resisting
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/CN2015/073920
Other languages
English (en)
French (fr)
Inventor
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 US15/310,318 priority Critical patent/US9845827B2/en
Priority to DE112015002746.7T priority patent/DE112015002746B4/de
Publication of WO2015188640A1 publication Critical patent/WO2015188640A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
    • F16C27/066—Ball or roller bearings
    • 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
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
    • F16C33/7823—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region of 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/768—Sealings of ball or roller bearings between relatively stationary parts, i.e. static seals
    • 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
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/164—Sealings between relatively-moving surfaces the sealing action depending on movements; pressure difference, temperature or presence of leaking fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3248—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports
    • F16J15/3252—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports
    • F16J15/3256—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports comprising two casing or support elements, one attached to each surface, e.g. cartridge or cassette seals
    • F16J15/3264—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports comprising two casing or support elements, one attached to each surface, e.g. cartridge or cassette seals the elements being separable from each other
    • 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
    • F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
    • F16C2208/10—Elastomers; Rubbers

Definitions

  • the invention relates to a bearing.
  • bearing seals are classified into contact seals and non-contact seals.
  • 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 contact seal has the advantage of good sealing effect, but it has the disadvantage that it is not suitable for sealing the bearing under high-speed rotation condition because the friction structure generates a large friction torque between the sealing structure and other components in the bearing. A large amount of heat is generated to accelerate the aging of the sealing structure, and also causes severe wear on the sealing structure, resulting in a reduced service life of the sealing structure.
  • the non-contact seal has the advantage of being suitable for sealing bearings under high-speed rotation conditions, but has the disadvantage of poor sealing.
  • the sealing structure of the existing bearing can only achieve contact sealing or can only achieve non-contact sealing, and can not realize the advantages of contact sealing and non-contact sealing at the same time, which is just some bearings with strict sealing requirements. (such as motor driven hub bearings) is not expected.
  • the problem to be solved by the present invention is that the sealing structure of the existing bearing cannot realize the advantages of the contact seal and the non-contact seal at the same time.
  • the present invention provides a bearing comprising: a non-rotating inner ring; a rotating outer ring; a sealing structure located in a radial gap between the inner ring and the outer ring, and sealing the bearing at an axial end of the bearing; the sealing structure comprising a static sealing ring and a coaxial sleeve a seal ring; the static seal ring is fixed to the outer peripheral surface of the inner ring and includes a contact ring extending radially along the bearing; the dynamic seal ring includes an annular body portion and an elastic seal; the body portion includes a bearing shaft a resisting ring extending and fixed on an inner circumferential surface of the outer ring, and a connecting ring connected to the resisting ring and located radially inward of the resisting ring, the connecting ring being located axially inside the contact ring
  • the resisting ring, the connecting ring and the contact ring enclose an inner cavity, the elastic sealing member is fixed to the connecting ring and includes
  • the elastic seal comprises a root fixed on the connecting ring, and a thin waist connecting the root and the sealing lip, the thin waist having a thickness smaller than a thickness of the sealing lip, the sealing lip It can rotate around the thin waist.
  • the connecting ring includes a first suspension ring extending axially along the bearing, and a transition ring connecting the resisting ring and the first suspension ring extending radially along the bearing, the first floating ring and The resisting rings are disposed at opposite radial intervals along the bearing, and the root is fixed to the first suspended ring.
  • the static seal ring further includes a retaining ring extending from the radially inner circumference of the contact ring along the axial direction of the bearing and fixed on the outer peripheral surface of the inner ring, and a radial outer periphery from the contact ring a second suspension ring extending along the axial direction of the bearing, the second suspension ring is opposite to the extending direction of the retaining ring; the first suspension ring and the retaining ring are oppositely disposed along the radial direction of the bearing and form a non-contact type Sealing, the resisting ring and the second suspension ring are radially disposed opposite each other along the bearing and form a non-contact seal.
  • the root of the elastic seal is provided with: a first labyrinth seal ring located in a radial interval between the first suspension ring and the retaining ring; the sealing structure further comprises: A labyrinth seal ring is located in a radial interval between the resist ring and the second suspension ring and is fixed to the second suspension ring.
  • the end of the resisting ring adjacent to the connecting ring has a tapered hole whose diameter gradually increases from the axial inner end of the resisting ring to the axial outer end.
  • the present invention also provides another bearing, comprising: a rotating inner ring; a non-rotating outer ring; a sealing structure located in a radial gap between the inner ring and the outer ring, and in the bearing
  • the elastic seal comprises a root fixed on the connecting ring, and a thin waist connecting the root and the sealing lip, the thin waist having a thickness smaller than a thickness of the sealing lip, the sealing lip It can rotate around the thin waist.
  • the connecting ring includes a first retaining ring extending along the axial direction of the bearing and fixed on the outer peripheral surface of the inner ring, and a transition ring connecting the first retaining ring and the resisting ring, the first retaining ring The base of the elastic seal is fixed to the first retaining ring.
  • the static seal ring further includes a second retaining ring extending from the radially outer periphery of the contact ring along the axial direction of the bearing and fixed on the inner circumferential surface of the outer ring, and a diameter from the contact ring a suspended ring extending axially in the axial direction of the bearing, an extension of the suspended ring and the second retaining ring
  • the first retaining ring and the floating ring are oppositely disposed along the radial interval of the bearing and form a non-contact seal
  • the resisting ring and the second retaining ring are oppositely disposed along the bearing radial interval and form a non-contact. Sealed.
  • the sealing structure further includes: a first labyrinth sealing ring located in a radial interval between the first retaining ring and the suspended ring, and fixed on the hanging ring; a second labyrinth sealing ring, Located in a radial interval between the resisting ring and the second retaining ring, and fixed to the resisting ring.
  • the resisting ring has a tapered hole whose diameter gradually decreases from an axial inner end of the resisting ring to an axial outer end.
  • the sealing lip contacts the contact ring and has a radial gap with the resisting ring, so that the elastic sealing member is in contact with the static sealing ring.
  • Sealing which has the advantage of good sealing effect without generating large friction torque; in the case of high-speed rotation of the bearing, that is, under the condition that the rotation speed of the outer ring or the inner ring is greater than or equal to the critical value, the sealing lip is The centrifugal force acts to break off the contact ring and abut against the resisting ring, so that the elastic sealing member forms a non-contact seal with the static sealing ring, and has the advantage of being suitable for sealing the bearing under high-speed rotating conditions, thereby making the sealing in the technical solution of the present invention
  • the structure enables the advantages of both contact and non-contact seals.
  • Figure 1 is a partial axial cross-sectional view showing one of the axial ends of the bearing in the first embodiment of the present invention
  • Figure 2 is a partial axial cross-sectional view showing one of the axial ends of the bearing in the second embodiment of the present invention.
  • the axially outer end and the axially inner end mean that the annular member at the axial end of the bearing is at both ends of the bearing axial direction, and the bearing includes an inner ring, an outer ring, and between the inner ring and the outer ring.
  • Rolling elements (not described in the following examples, nor shown).
  • the axial outer end refers to an end which is relatively far away from the rolling body in the axial direction of the bearing;
  • the axial inner end refers to an end which is closer to the rolling body in the axial direction of the bearing.
  • the axial outer side refers to the side farther away from the rolling body in the axial direction of the bearing; the axial inner side refers to the side closer to the rolling element in the axial direction of the bearing.
  • the bearing of the present embodiment is an outer ring rotary bearing, comprising: a non-rotating inner ring 1; a rotating outer ring 2; a sealing structure 3, located in a radial direction between the inner ring 1 and the outer ring 2 Inside the gap (not identified), seal the bearing at the axial end of the bearing.
  • the sealing structure 3 includes a static sealing ring 31 and a dynamic sealing ring 32 that are coaxially sleeved.
  • the static seal ring 31 includes: a contact ring 311 extending radially in the bearing; a retaining ring 312 extending from the radially inner periphery of the contact ring 311 along the axial direction of the bearing and fixed to the outer peripheral surface of the inner ring 1; The second outer ring 313 extending radially in the axial direction of the bearing, the second flying ring 313 and the retaining ring 312 extend in opposite directions.
  • the contact ring 311, the retaining ring 312, and the second flying ring 313 are integrally formed, and the material is metal (such as stainless steel).
  • the dynamic seal ring 32 includes an annular body portion 321 and an elastic seal 322.
  • the material of the elastic seal 322 is rubber.
  • the body portion 321 includes a resisting ring 321a extending in the axial direction of the bearing and fixed to the inner peripheral surface of the outer ring 2, and a connecting ring 321b connected to the resisting ring 321a and located radially inward of the resisting ring 321a.
  • the connecting ring 321b is located on the axial inner side of the contact ring 311, and the resisting ring 321a, the connecting ring 321b, and the contact ring 311 enclose the inner cavity G.
  • the connecting ring 321b includes a first flying ring 321b1 extending along the axial direction of the bearing And connecting the resisting ring 321a and the transition ring 321b2 of the first suspension ring 321b1 extending in the radial direction of the bearing, the first suspension ring 321b1 and the resisting ring 321a are disposed opposite to each other in the radial direction of the bearing, and the elastic sealing member 322 is located in the inner cavity G and The root portion 322b is fixed to the first suspension ring 321b1, and the elastic sealing member 322 and the abutting ring 321a are disposed diametrically opposite to each other and include a sealing lip 322a protruding into the inner cavity G.
  • the radial arrangement of the first suspension ring 321b1 and the abutment ring 321a in the radial direction of the bearing means that the first suspension ring 321b1 and the abutment ring 321a are spaced apart in the radial direction of the bearing and have a facing area.
  • the resisting ring 321a, the first flying ring 321b1, and the transition ring 321b2 are integrally formed, and the material is metal (such as stainless steel).
  • the fact that the elastic seal 322 and the resisting ring 321a are disposed diametrically opposite to each other means that the elastic seal 322 and the resisting ring 321a have a facing area in the radial direction of the bearing.
  • the outer ring 2 of the bearing When the outer ring 2 of the bearing rotates, it will rotate together with the dynamic seal ring 32.
  • the sealing lip 322a of the elastic sealing member 322 In the case where the bearing rotates at a low speed, that is, under the condition that the rotational speed of the outer ring 2 is less than the critical value, the sealing lip 322a of the elastic sealing member 322 is in contact with the contact ring 311 and has a radial gap (not labeled) with the resisting ring 321a,
  • the elastic sealing member 322 and the static sealing ring 31 form a contact seal, which has the advantages of good sealing effect; in addition, since the elastic sealing member 322 and the static sealing ring 31 realize the contact sealing under the condition of low-speed rotation of the bearing, it does not generate Large friction torque.
  • the sealing lip 322a is disengaged from the contact ring 311 by the centrifugal force and abuts against the resisting ring 321a, so that the sealing lip 322a and the static seal are sealed.
  • the ring 31 forms a non-contact seal, and since the non-contact seal does not generate frictional torque, it has an advantage of being suitable for sealing a bearing under high-speed rotation conditions.
  • the critical value of the rotational speed of the outer ring 2 needs to be selected in consideration of the application of the bearing, the sealing effect of the bearing and the service life of the sealing structure, and the structure of the elastic sealing member 322 is designed accordingly.
  • the bearing is a motor driven hub bearing. Even if the rotational speed of the motor-driven hub bearing is as high as 40 m/s, the sealing structure 3 still has a good sealing effect.
  • the lubricant used in the bearing is a grease.
  • the first suspension ring 321b1 and the retaining ring 312 are disposed opposite to each other in the radial direction of the bearing, and the root portion 322b of the elastic seal 322 is provided with a first labyrinth seal located in a radial interval between the first suspension ring 321b1 and the retaining ring 312. Ring 33.
  • the first labyrinth seal ring 33 By providing the first labyrinth seal ring 33, the first suspension ring 321b1 and the retaining ring 312 form a labyrinth seal (one of the non-contact seals).
  • the resisting ring 321a and the second flying ring 313 are oppositely disposed along the radial direction of the bearing, and the second flying ring 313 is fixed with a second labyrinth sealing ring located in a radial interval between the resisting ring 321a and the second flying ring 313. 34.
  • the resist ring 321a and the second suspension ring 313 form a labyrinth seal.
  • the material of the first labyrinth seal ring 33 and the second labyrinth seal ring 34 is rubber.
  • the first suspension ring 321b1 and the contact ring 311 are spaced apart in the axial direction of the bearing and form a non-contact seal.
  • the non-contact seal formed by the first suspension ring 321b1 and the contact ring 311, and the non-contact seal formed by the first suspension ring 321b1 and the retaining ring 312 can be used as the first, second, third, respectively, to prevent external pollutants from entering the bearing.
  • the formed contact seal (or a non-contact seal formed under the condition of high-speed rotation of the bearing), the non-contact seal formed by the resist ring 321a and the second suspension ring 313 can be sequentially used as the first to prevent lubricant leakage in the bearing, Second, third and fourth lines of defense.
  • the non-contact seal formed by the addition of the resisting ring 321a and the second suspension ring 313, the non-contact seal formed by the first suspension ring 321b1 and the contact ring 311, and the first suspension ring 321b1 are
  • the non-contact seal formed by the retaining ring 312 can improve the sealing effect of the sealing structure 3.
  • the first suspension ring 321b1 and the contact ring 311 are spaced apart in the axial direction of the bearing, but a non-contact seal is not formed.
  • the sealing structure 3 is provided with three lines of defense to achieve the seal.
  • the elastic seal 322 and the static seal ring 31 form a contact seal
  • the inner cavity G is divided into two non-intersecting inner cavity units, respectively a first inner cavity unit G1 and a second inner cavity.
  • the first inner cavity unit G1 communicates with the radial gap between the resisting ring 321a and the second flying ring 313, and the second inner cavity unit G2 communicates with the radial gap between the first floating ring 321b1 and the retaining ring 312.
  • the second inner cavity unit G2 communicates with the radial gap between the resisting ring 321a and the second floating ring 313, even if external contaminants enter between the resisting ring 321a and the second floating ring 313. Radial clearance, external pollutants are also difficult to enter the second cavity unit G2 due to centrifugal force, and it is less likely to enter the radial gap between the first suspension ring 321b1 and the holding ring 312, thereby preventing external pollutants from entering the bearing.
  • the sealing effect of the sealing structure 3 is further enhanced.
  • the first labyrinth seal ring 33 has four annular seal teeth 330 and the second labyrinth seal ring 34 has three annular seal teeth 340. It should be noted that the number of the annular seal teeth 330 in the first labyrinth seal ring 33 and the annular seal teeth 340 in the second labyrinth seal ring 34 should not be limited to the embodiment, and can be adjusted according to the sealing requirements. When the number of the two is greater, the sealing effect is better.
  • the annular sealing teeth 330 and the annular sealing teeth 340 have a semi-cylindrical cross section.
  • the shapes of the annular seal teeth 330 and the annular seal teeth 340 are not limited to the embodiment, and may be provided in other shapes.
  • the first labyrinth seal ring 33 and the second labyrinth seal ring 34 may not be provided.
  • the first flying ring 321b1 and the holding can also be realized.
  • the ring 312 forms a non-contact seal
  • the resisting ring 321a forms a non-contact seal with the second suspended ring 313.
  • the first labyrinth seal ring 33 may not be located in the bullet.
  • the root portion 322b of the sealing member 322 is fixed to the retaining ring 312; the second labyrinth sealing ring 34 may also be fixed to the resisting ring 321a.
  • the elastic seal 322 further includes a thin waist portion 322c connecting the root portion 322b and the sealing lip 322a.
  • the thickness of the thin waist portion 322c is smaller than the thickness of the sealing lip 322a such that the center of gravity of the elastic sealing member 322 is located on the sealing lip 322a.
  • the sealing lip 322a By providing the thin waist portion 322c in the elastic sealing member 322, not only the sealing lip 322a can be rotated around the thin waist portion 322c in the case where the bearing is rotated at a high speed, so that the sealing lip 322a is more easily detached from the static sealing ring 31; In the case where the bearing rotates at a high speed, the sealing lip 322a itself does not undergo bending deformation due to the rotation; moreover, it is also possible to make it easier to recover the sealing lip 322a against the resisting ring 321a when the bearing is switched from high speed rotation to low speed rotation. To the state in contact with the contact ring 311.
  • the thickness of the thin waist portion 322c is smaller than the thickness of the sealing lip 322a. It means that the elastic sealing member 322 is cut by an axial section. On the cross section of the obtained elastic sealing member 322, the size of the thin waist portion 322c in the axial direction of the bearing is smaller than that of the sealing lip 322a. In the axial direction of the bearing, the axis of the bearing lies on the axial section.
  • the end of the resisting ring 321a adjacent to the connecting ring 321b has a tapered hole (not labeled) whose diameter gradually increases from the axial inner end of the resisting ring 321a to the axial outer end direction, so that the resisting ring 321a is close to the connection.
  • One end of the ring 321b has a slope shape.
  • the slope can prevent the sealing lip 322a from being bent in a radially inward direction, preventing the sealing lip 322a from returning to the contact ring when the bearing is switched from high speed rotation to low speed rotation.
  • external pollutants such as sewage
  • external pollutants can slide down the slope under their own gravity, so that they can be easily leaked from the inner cavity G. .
  • the axial gap S between the elastic seal 322 and the portion of the contact ring 311 located radially inward of the contact position there is an axial gap S between the elastic seal 322 and the portion of the contact ring 311 located radially inward of the contact position.
  • the axial gap S between the elastic seal member 322 and the contact ring 311 gradually decreases in the radially outward direction B of the bearing.
  • the resisting ring 321a is provided with a seal ring O between the portion of the first suspension ring 321b1 and the outer ring 2 to prevent leakage of lubricant in the bearing from between the resist ring 321a and the outer ring 2.
  • the material of the seal ring O is rubber.
  • the bearing of this embodiment is an inner ring rotary bearing, comprising: a rotating inner ring 4; a non-rotating outer ring 5; a sealing structure 6, located in a radial direction between the inner ring 4 and the outer ring 5. Inside the gap, seal the bearing at the axial end of the bearing.
  • the sealing structure 6 includes a static sealing ring 61 and a dynamic sealing ring 62 that are coaxially sleeved.
  • the static seal ring 61 includes: a contact ring 611 extending radially in the bearing; a second retaining ring 612 extending from the radially outer periphery of the contact ring 611 in the axial direction of the bearing and fixed to the inner peripheral surface of the outer ring 5, and The radially inner circumference of the contact ring 611 extends along the axial direction of the bearing, and the suspension ring 613 and the second holding ring 612 extend in opposite directions.
  • the dynamic seal ring 62 includes an annular body portion 621 and an elastomeric seal 622.
  • the main body portion 621 includes a connecting ring 621b fixed to the outer circumferential surface of the inner ring 4, and a resisting ring 621a connected to the connecting ring 621b and located radially outward of the connecting ring 621b.
  • the resisting ring 621a extends in the axial direction of the bearing and the inner ring 4 There is a radial spacing, the resisting ring 621a is located on the axially outer side of the contact ring 611, and the connecting ring 621b, the resisting ring 621a and the contact ring 611 enclose the inner cavity G.
  • the connecting ring 621b includes: a first retaining ring 621b1 extending along the axial direction of the bearing and fixed on the outer peripheral surface of the inner ring 4, and a transition ring 621b2 connecting the first retaining ring 621b1 and the resisting ring 621a, the first retaining ring 621b1
  • the elastic sealing member 622 is disposed in the inner cavity G and the root portion 622b is fixed on the first retaining ring 621b1, and the elastic sealing member 622 and the resisting ring 621a are disposed opposite to each other in the radial direction of the bearing, and A sealing lip 622a that protrudes into the lumen G is included.
  • the inner ring 4 of the bearing When the inner ring 4 of the bearing rotates, it will rotate together with the dynamic seal ring 62.
  • the sealing lip 622a of the elastic sealing member 622 In the case where the bearing rotates at a low speed, that is, under the condition that the rotational speed of the inner ring 4 is less than the critical value, the sealing lip 622a of the elastic sealing member 622 is in contact with the contact ring 611 and exists with the resisting ring 621a.
  • the radial gap (not labeled) forms a contact seal between the elastic seal 622 and the static seal ring 61, and has the advantage of good sealing effect.
  • the sealing lip 622a is disengaged from the contact ring 611 by the centrifugal force and abuts against the resisting ring 621a, so that the sealing lip 622a and the static seal are sealed.
  • the ring 61 forms a non-contact seal, and since the non-contact seal does not generate frictional torque, it has an advantage of being suitable for sealing a bearing under high-speed rotation conditions.
  • the first retaining ring 621b1 and the suspension ring 613 are oppositely disposed along the radial direction of the bearing, and the first labyrinth seal ring 63 is disposed on the suspension ring 613 in a radial interval between the first retaining ring 621b1 and the suspended ring 613.
  • the resisting ring 621a and the second retaining ring 612 are oppositely disposed along the radial direction of the bearing, and the resisting ring 621a is fixed with a second labyrinth sealing ring 64 located in a radial interval between the resisting ring 621a and the second retaining ring 612.
  • the resisting ring 621a and the contact ring 611 are spaced apart in the axial direction of the bearing and form a non-contact seal.
  • the first labyrinth seal ring 63, the second labyrinth seal ring 64, and the contact ring 621a and the contact ring 611 form a non-contact seal. Referring to the first embodiment, details are not described herein.
  • the first labyrinth seal ring 63 and the second labyrinth seal ring 64 may be omitted, and the first retaining ring 621b1 and the suspension ring 613 may be directly formed into a non-contact seal.
  • the resisting ring 621a and the second retaining ring 612 form a non-contact seal.
  • the resisting ring 621a and the contact ring 611 are spaced apart in the axial direction of the bearing, but a non-contact seal is not formed.
  • the axial gap S between the elastic seal 622 and the contact ring 611 gradually decreases in the radially outward direction B of the bearing.
  • the resisting ring 621a has an inner end from the axial end of the resisting ring 621a to the shaft.
  • a tapered hole (not labeled) whose diameter gradually decreases toward the outer end direction causes the resisting ring 621a to have a slope shape.
  • the shape of the static sealing ring, the connecting ring in the annular body portion, the shape of the elastic sealing member, and the position of the elastic sealing member fixed on the connecting ring are not limited to Give the example.
  • 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.

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Abstract

一种轴承，包括：非转动的内圈；转动的外圈；密封结构，位于内、外圈之间的径向间隙内并包括同轴套设的静、动密封环；静密封环固设于内圈外周面并包括接触环；动密封环包括环形本体部和弹性密封件；本体部包括抵挡环、及与抵挡环连接并位于其径向内侧的连接环，连接环位于接触环的轴向内侧，抵挡环、连接环与接触环围成内腔，弹性密封件固设于连接环并包括突伸至内腔中的密封唇；外圈的旋转速度小于临界值时，密封唇与接触环接触并与抵挡环存在径向间隙；外圈的旋转速度不小于临界值时，密封唇脱离接触环并抵靠抵挡环，使密封唇与静密封环形成非接触式密封。解决了现有轴承的密封结构无法同时实现接触式密封和非接触式密封的优点的问题。

Description

轴承
本申请要求2014年6月11日提交中国专利局、申请号为201410258106.1、发明名称为“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
本发明涉及一种轴承。
背景技术
现有轴承密封分为接触式密封和非接触式密封两种。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。
接触式密封具有密封效果好的优点，但却存在不适合对高速旋转条件下的轴承进行密封的缺点，原因在于：密封结构与轴承内的其他部件之间会产生较大的摩擦转矩，不仅会产生大量的热量以致加速密封结构的老化，而且还会对密封结构造成较为严重的磨损，导致密封结构的使用寿命减少。
非接触式密封具有适合对高速旋转条件下的轴承进行密封的优点，但却存在密封效果不佳的缺点。
现有轴承的密封结构要么只能实现接触式密封、要么只能实现非接触式密封，无法同时实现接触式密封和非接触式密封的优点，而这恰是某些对密封要求比较苛刻的轴承(如电机驱动轮毂轴承)所不期望的。
发明内容
本发明要解决的问题是：现有轴承的密封结构无法同时实现接触式密封和非接触式密封的优点。
为解决上述问题，本发明提供了一种轴承，包括：非转动的内圈； 转动的外圈；密封结构，位于所述内圈与外圈之间的径向间隙内，并在轴承的轴向端部密封轴承；所述密封结构包括同轴套设的静密封环和动密封环；所述静密封环固设于所述内圈外周面并包括沿轴承径向延伸的接触环；所述动密封环包括环形本体部和弹性密封件；所述本体部包括沿轴承轴向延伸并固设于外圈内周面上的抵挡环、及与所述抵挡环连接并位于所述抵挡环径向内侧的连接环，所述连接环位于所述接触环的轴向内侧，所述抵挡环、连接环与所述接触环围成内腔，所述弹性密封件固设于所述连接环并包括突伸至所述内腔中的密封唇；在所述外圈的旋转速度小于临界值的条件下，所述弹性密封件的密封唇与所述接触环接触，并与所述抵挡环存在径向间隙；在所述外圈的旋转速度大于等于所述临界值的条件下，所述密封唇在离心力的作用下脱离所述接触环并抵靠所述抵挡环，使所述密封唇与所述静密封环形成非接触式密封。
可选的，所述弹性密封件包括固定在所述连接环上的根部、及连接所述根部与密封唇的细腰部，所述细腰部的厚度小于所述密封唇的厚度，所述密封唇能绕所述细腰部转动。
可选的，所述连接环包括沿轴承轴向延伸的第一悬空环、及连接所述抵挡环与所述第一悬空环的沿轴承径向延伸的过渡环，所述第一悬空环与抵挡环沿轴承径向间隔相对设置，所述根部固定在所述第一悬空环上。
可选的，所述静密封环还包括自所述接触环的径向内周缘沿轴承轴向延伸并固设于内圈外周面上的固持环、及自所述接触环的径向外周缘沿轴承轴向延伸的第二悬空环，所述第二悬空环与所述固持环的延伸方向相反；所述第一悬空环、所述固持环沿轴承径向间隔相对设置并形成非接触式密封，所述抵挡环、所述第二悬空环沿轴承径向间隔相对设置并形成非接触式密封。
可选的，所述弹性密封件的根部设有：位于所述第一悬空环与固持环之间的径向间隔内的第一迷宫密封环；所述密封结构还包括：第 二迷宫密封环，位于所述抵挡环与第二悬空环之间的径向间隔内，并固定在所述第二悬空环上。
可选的，所述抵挡环靠近所述连接环的一端具有：自所述抵挡环轴向内端至轴向外端方向直径逐渐增大的锥形孔。
为解决上述问题，本发明还提供了另一种轴承，包括：转动的内圈；非转动的外圈；密封结构，位于所述内圈与外圈之间的径向间隙内，并在轴承的轴向端部密封轴承；所述密封结构包括同轴套设的静密封环和动密封环；所述静密封环固设于所述外圈内周面并包括沿轴承径向延伸的接触环；所述动密封环包括环形本体部和弹性密封件；所述本体部包括固设于内圈外周面上的连接环、及与所述连接环连接并位于所述连接环径向外侧的抵挡环，所述抵挡环沿轴承轴向延伸并与所述内圈存在径向间隔，所述抵挡环位于接触环的轴向外侧，所述连接环、抵挡环与所述接触环围成内腔，所述弹性密封件固设于所述连接环并包括突伸至所述内腔中的密封唇；在所述内圈的旋转速度小于临界值的条件下，所述弹性密封件的密封唇与所述接触环接触，并与所述抵挡环存在径向间隙；在所述内圈的旋转速度大于等于所述临界值的条件下，所述密封唇在离心力的作用下脱离所述接触环并抵靠所述抵挡环，使所述密封唇与所述静密封环形成非接触式密封。
可选的，所述弹性密封件包括固定在所述连接环上的根部、及连接所述根部与密封唇的细腰部，所述细腰部的厚度小于所述密封唇的厚度，所述密封唇能绕所述细腰部转动。
可选的，所述连接环包括沿轴承轴向延伸并固设于内圈外周面上的第一固持环、及连接所述第一固持环与抵挡环的过渡环，所述第一固持环与抵挡环沿轴承径向相对设置，所述弹性密封件的根部固设于所述第一固持环上。
可选的，所述静密封环还包括自所述接触环的径向外周缘沿轴承轴向延伸并固设于外圈内周面上的第二固持环、及自所述接触环的径向内周缘沿轴承轴向延伸的悬空环，所述悬空环与第二固持环的延伸 方向相反；所述第一固持环、所述悬空环沿轴承径向间隔相对设置并形成非接触式密封，所述抵挡环、所述第二固持环沿轴承径向间隔相对设置并形成非接触式密封。
可选的，所述密封结构还包括：第一迷宫密封环，位于所述第一固持环与悬空环之间的径向间隔内，并固定在所述悬空环上；第二迷宫密封环，位于所述抵挡环与第二固持环之间的径向间隔内，并固定在所述抵挡环上。
可选的，所述抵挡环具有：自所述抵挡环轴向内端至轴向外端方向直径逐渐减小的锥形孔。
与现有技术相比，本发明的技术方案具有以下优点：
在轴承低速旋转的情况下，也就是外圈或内圈的旋转速度小于临界值的条件下，密封唇与接触环接触并与抵挡环存在径向间隙，使弹性密封件与静密封环形成接触式密封，在不会产生较大摩擦转矩的同时具有密封效果好的优点；在轴承高速旋转的情况下，也就是外圈或内圈的旋转速度大于等于临界值的条件下，密封唇在离心力的作用下脱离接触环并抵靠抵挡环，使弹性密封件与静密封环形成非接触式密封，具有适合对高速旋转条件下的轴承进行密封的优点，进而使得本发明技术方案中的密封结构能够同时实现接触式密封和非接触式密封的优点。
附图说明
图1是本发明的第一实施例中轴承其中一个轴向端部的局部轴向截面示意图；
图2是本发明的第二实施例中轴承其中一个轴向端部的局部轴向截面示意图。
具体实施方式
技术术语解释：
轴向外端、轴向内端是指：位于轴承轴向端部的环形部件在轴承轴向上的两端，所述轴承包括内圈、外圈、以及位于内圈和外圈之间的滚动体(下述实施例中未文字描述、也未图示)。其中，轴向外端：是指在轴承轴向上较为远离滚动体的一端；轴向内端：是指在轴承轴向上较为靠近滚动体的一端。
轴向外侧：是指在轴承轴向上较为远离滚动体的一侧；轴向内侧：是指在轴承轴向上较为靠近滚动体的一侧。
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1所示，本实施例的轴承为外圈旋转式轴承，包括：非转动的内圈1；转动的外圈2；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。密封结构3包括：同轴套设的静密封环31和动密封环32。
静密封环31包括：沿轴承径向延伸的接触环311；自接触环311的径向内周缘沿轴承轴向延伸并固设于内圈1外周面上的固持环312；自接触环311的径向外周缘沿轴承轴向延伸的第二悬空环313，第二悬空环313和固持环312的延伸方向相反。在具体实施例中，接触环311、固持环312以及第二悬空环313一体成型，材料为金属(如不锈钢)。
动密封环32包括：环形本体部321和弹性密封件322。在本实施例中，弹性密封件322的材料为橡胶。本体部321包括：沿轴承轴向延伸并固设于外圈2内周面上的抵挡环321a；与抵挡环321a连接并位于抵挡环321a径向内侧的连接环321b。连接环321b位于接触环311的轴向内侧，抵挡环321a、连接环321b与接触环311围成内腔G。
其中，连接环321b包括沿轴承轴向延伸的第一悬空环321b1、 及连接抵挡环321a与第一悬空环321b1的沿轴承径向延伸的过渡环321b2，第一悬空环321b1与抵挡环321a沿轴承径向间隔相对设置，弹性密封件322位于内腔G内且其根部322b固定在第一悬空环321b1上，弹性密封件322与抵挡环321a沿轴承径向相对设置，并包括突伸至内腔G中的密封唇322a。
第一悬空环321b1与抵挡环321a沿轴承径向间隔相对设置是指：第一悬空环321b1与抵挡环321a在轴承径向上间隔排列，且具有正对面积。在具体实施例中，抵挡环321a、第一悬空环321b1、以及过渡环321b2一体成型，材料为金属(如不锈钢)。弹性密封件322与抵挡环321a沿轴承径向相对设置是指：弹性密封件322与抵挡环321a在轴承径向上具有正对面积。
轴承的外圈2旋转时，会带着动密封环32一起旋转。在轴承低速旋转的情况下，也就是外圈2的旋转速度小于临界值的条件下，弹性密封件322的密封唇322a与接触环311接触并与抵挡环321a存在径向间隙(未标识)，使弹性密封件322与静密封环31形成接触式密封，具有密封效果好的优点；另外，由于弹性密封件322与静密封环31是在轴承低速旋转情况下实现接触式密封，故不会产生较大的摩擦转矩。
在轴承高速旋转的情况下，也就是外圈2的旋转速度大于等于临界值的条件下，密封唇322a在离心力的作用下脱离接触环311并抵靠抵挡环321a，使密封唇322a与静密封环31形成非接触式密封，由于非接触式密封不会产生摩擦转矩，因而具有适合对高速旋转条件下的轴承进行密封的优点。
外圈2旋转速度的临界值需综合考虑轴承的应用场合、轴承对密封效果以及密封结构使用寿命的要求进行选择，并据此来设计弹性密封件322的结构。
在本实施例中，轴承为电机驱动轮毂轴承。即使电机驱动轮毂轴承的旋转速度高达至40m/s，密封结构3依然具有良好的密封效果。
在本发明的技术方案中，所述轴承所采用的润滑剂为润滑脂。
第一悬空环321b1、固持环312沿轴承径向间隔相对设置，且弹性密封件322的根部322b设有：位于第一悬空环321b1与固持环312之间的径向间隔内的第一迷宫密封环33。通过设置第一迷宫密封环33，使得第一悬空环321b1与固持环312形成迷宫式密封(非接触式密封中的一种)。
抵挡环321a、第二悬空环313沿轴承径向间隔相对设置，且第二悬空环313上固设有位于抵挡环321a与第二悬空环313之间的径向间隔内的第二迷宫密封环34。通过设置第二迷宫密封环34，使得抵挡环321a与第二悬空环313形成迷宫式密封。第一迷宫密封环33、第二迷宫密封环34的材料为橡胶。
第一悬空环321b1与接触环311在轴承轴向上存在间隔并形成非接触式密封。
抵挡环321a与第二悬空环313形成的非接触式密封、密封唇322a与静密封环31在轴承低速旋转情况下形成的接触式密封(或者在轴承高速旋转情况下形成的非接触式密封)、第一悬空环321b1与接触环311形成的非接触式密封、第一悬空环321b1与固持环312形成的非接触式密封能够依次作为防止外界污染物进入轴承内的第一、二、三、四道防线，第一悬空环321b1与固持环312形成的非接触式密封、第一悬空环321b1与接触环311形成的非接触式密封、密封唇322a与静密封环31在轴承低速旋转情况下形成的接触式密封(或者在轴承高速旋转情况下形成的非接触式密封)、抵挡环321a与第二悬空环313形成的非接触式密封能够依次作为防止轴承内的润滑剂泄露的第一、二、三、四道防线。
由上述分析可知，密封结构3中通过增加抵挡环321a与第二悬空环313形成的非接触式密封、第一悬空环321b1与接触环311形成的非接触式密封、以及第一悬空环321b1与固持环312形成的非接触式密封，能够提高密封结构3的密封效果。
在本实施例的变换例中，第一悬空环321b1与接触环311在轴承轴向上存在间隔，但并未形成非接触式密封。在这种情况下，密封结构3设置三道防线来实现密封。
在轴承低速旋转的情况下，弹性密封件322和静密封环31形成接触式密封，并将内腔G分隔为两个不相通的内腔单元，分别为第一内腔单元G1、第二内腔单元G2。其中，第一内腔单元G1与抵挡环321a与第二悬空环313之间的径向间隙相通，第二内腔单元G2与第一悬空环321b1与固持环312之间的径向间隙相通。在轴承高速旋转的情况下，第二内腔单元G2与抵挡环321a与第二悬空环313之间的径向间隙相通，即使外界污染物有进入抵挡环321a与第二悬空环313之间的径向间隙，外界污染物也因离心力很难进入第二内腔单元G2，更不容易进入第一悬空环321b1与固持环312之间的径向间隙，进而能够阻止外界污染物进入轴承内，进一步加强了密封结构3的密封效果。
第一迷宫密封环33具有四个环形密封齿330，第二迷宫密封环34具有三个环形密封齿340。需说明的是，第一迷宫密封环33中环形密封齿330、以及第二迷宫密封环34中环形密封齿340的数量均不应局限于本实施例，可以根据密封要求来作调整。当两者的数量越多时，密封效果越佳。
环形密封齿330、环形密封齿340的轴向截面均呈半圆柱型。但是，环形密封齿330、环形密封齿340的形状均不应局限于本实施例，也可以设置为其他形状。
在本实施例的变换例中，也可以没有第一迷宫密封环33、第二迷宫密封环34。在这种情况下，通过设置第一悬空环321b1与固持环312之间的径向间隙、抵挡环321a与第二悬空环313之间的径向间隙，也可以实现第一悬空环321b1与固持环312形成非接触式密封、抵挡环321a与第二悬空环313形成非接触式密封。
在本实施例的变换例中，第一迷宫密封环33也可以不是位于弹 性密封件322的根部322b上，而是固设于固持环312上；第二迷宫密封环34也可以固设于抵挡环321a上。
弹性密封件322还包括：连接根部322b与密封唇322a的细腰部322c，细腰部322c的厚度小于密封唇322a的厚度，使得弹性密封件322的重心位于密封唇322a上。通过在弹性密封件322中设置细腰部322c，不仅使得在轴承高速旋转的情况下，密封唇322a能够绕着细腰部322c旋转，使得密封唇322a更容易脱离静密封环31；而且，还使得在轴承高速旋转的情况下，密封唇322a自身不会因旋转而发生弯曲形变；而且，还可以使得在轴承由高速旋转转换至低速旋转时，抵靠在抵挡环321a上的密封唇322a更容易恢复至与接触环311接触的状态。
细腰部322c的厚度小于密封唇322a的厚度是指：利用一轴向截面剖切弹性密封件322，在所得弹性密封件322的截面上，细腰部322c在轴承轴向上的尺寸小于密封唇322a在轴承轴向上的尺寸，轴承的轴线位于所述轴向截面上。
在本实施例中，抵挡环321a靠近连接环321b的一端具有：自抵挡环321a轴向内端至轴向外端方向直径逐渐增大的锥形孔(未标识)，使得抵挡环321a靠近连接环321b的一端呈斜坡状。在密封唇322a脱离静密封环31时，该斜坡可以阻止密封唇322a向径向向内的方向弯折，防止在在轴承由高速旋转转换至低速旋转时，密封唇322a不能恢复至与接触环311接触的状态；另一方面，即使外界污染物(如污水)有进入内腔G，外界污染物也能够在自身重力作用下沿着该斜坡滑落，从而能够很容易地从内腔G泄露出去。
在外圈2的旋转速度小于临界值的条件下，弹性密封件322和接触环311位于接触位置径向内侧的部分之间存在轴向间隙S。在本实施例中，弹性密封件322和接触环311之间的轴向间隙S沿轴承径向向外的方向B逐渐减小。在密封唇322a因离心力脱离静密封环31时，即使第二内腔单元G2内有外界污染物，第二内腔单元G2内的 外界污染物也能够更容易在离心力的作用下从轴向间隙S甩出。
在本实施例中，抵挡环321a正对第一悬空环321b1的部分和外圈2之间套设有密封环O，以防止轴承内的润滑剂从抵挡环321a和外圈2之间泄露。在本实施例中，密封环O的材料为橡胶。
第二实施例
如图2所示，本实施例的轴承为内圈旋转式轴承，包括：转动的内圈4；非转动的外圈5；密封结构6，位于内圈4与外圈5之间的径向间隙内，并在轴承的轴向端部密封轴承。密封结构6包括：同轴套设的静密封环61和动密封环62。
静密封环61包括：沿轴承径向延伸的接触环611；自接触环611的径向外周缘沿轴承轴向延伸并固设于外圈5内周面上的第二固持环612、及自接触环611的径向内周缘沿轴承轴向延伸的悬空环613，悬空环613与第二固持环612的延伸方向相反。
动密封环62包括环形本体部621和弹性密封件622。本体部621包括固设于内圈4外周面上的连接环621b、及与连接环621b连接并位于连接环621b径向外侧的抵挡环621a，抵挡环621a沿轴承轴向延伸并与内圈4存在径向间隔，抵挡环621a位于接触环611的轴向外侧，连接环621b、抵挡环621a与接触环611围成内腔G。
其中，连接环621b包括：沿轴承轴向延伸并固设于内圈4外周面上的第一固持环621b1、及连接第一固持环621b1与抵挡环621a的过渡环621b2，第一固持环621b1与抵挡环621a沿轴承径向相对设置，弹性密封件622位于内腔G内且其根部622b固设于第一固持环621b1上，弹性密封件622与抵挡环621a沿轴承径向相对设置，并包括突伸至内腔G中的密封唇622a。
轴承的内圈4旋转时，会带着动密封环62一起旋转。在轴承低速旋转的情况下，也就是内圈4的旋转速度小于临界值的条件下，弹性密封件622的密封唇622a与接触环611接触并与抵挡环621a存在 径向间隙(未标识)，使弹性密封件622与静密封环61形成接触式密封，具有密封效果好的优点。
在轴承高速旋转的情况下，也就是内圈4的旋转速度大于等于临界值的条件下，密封唇622a在离心力的作用下脱离接触环611并抵靠抵挡环621a，使密封唇622a与静密封环61形成非接触式密封，由于非接触式密封不会产生摩擦转矩，因而具有适合对高速旋转条件下的轴承进行密封的优点。
第一固持环621b1、悬空环613沿轴承径向间隔相对设置，且悬空环613上固设有位于第一固持环621b1与悬空环613之间的径向间隔内的第一迷宫密封环63。抵挡环621a、第二固持环612沿轴承径向间隔相对设置，且抵挡环621a上固设有位于抵挡环621a与第二固持环612之间的径向间隔内的第二迷宫密封环64。抵挡环621a与接触环611在轴承轴向上存在间隔并形成非接触式密封。
第一迷宫密封环63、第二迷宫密封环64、以及抵挡环621a与接触环611形成非接触式密封的作用参考第一实施例，在此不再赘述。
同第一实施例一样，在第二实施例的变换例中，也可以没有第一迷宫密封环63、第二迷宫密封环64，直接使第一固持环621b1与悬空环613形成非接触式密封、抵挡环621a与第二固持环612形成非接触式密封。
同第一实施例一样，在第二实施例的变换例中，抵挡环621a与接触环611在轴承轴向上存在间隔，但并未形成非接触式密封。
动密封环62中弹性密封件622的结构可以参考第一实施例，在此不再赘述。
在本实施例中，弹性密封件622和接触环611之间的轴向间隙S沿轴承径向向外的方向B逐渐减小。这样设置所带来的有益效果请参考第一实施例，在此不再赘述。
在本实施例中，抵挡环621a具有：自抵挡环621a轴向内端至轴 向外端方向直径逐渐减小的锥形孔(未标识)，使得抵挡环621a呈斜坡状。在本实施例中抵挡环621a设置成此形状所带来的效果请参考第一实施例，在此不再赘述。
需说明的是，在本发明的技术方案中，静密封环、环形本体部中的连接环、弹性密封件的形状，以及弹性密封件固设于连接环上的位置并不应仅局限于所给实施例。
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 (12)

  1. 一种轴承，包括：非转动的内圈；转动的外圈；密封结构，位于所述内圈与外圈之间的径向间隙内，并在轴承的轴向端部密封轴承；
    其特征在于，所述密封结构包括：同轴套设的静密封环和动密封环；
    所述静密封环固设于所述内圈外周面并包括沿轴承径向延伸的接触环；
    所述动密封环包括环形本体部和弹性密封件；
    所述本体部包括沿轴承轴向延伸并固设于外圈内周面上的抵挡环、及与所述抵挡环连接并位于所述抵挡环径向内侧的连接环，所述连接环位于所述接触环的轴向内侧，所述抵挡环、连接环与所述接触环围成内腔，所述弹性密封件固设于所述连接环并包括突伸至所述内腔中的密封唇；
    在所述外圈的旋转速度小于临界值的条件下，所述弹性密封件的密封唇与所述接触环接触，并与所述抵挡环存在径向间隙；
    在所述外圈的旋转速度大于等于所述临界值的条件下，所述密封唇在离心力的作用下脱离所述接触环并抵靠所述抵挡环，使所述密封唇与所述静密封环形成非接触式密封。
  2. 如权利要求1所述的轴承，其特征在于，所述弹性密封件包括固定在所述连接环上的根部、及连接所述根部与密封唇的细腰部，所述细腰部的厚度小于所述密封唇的厚度，所述密封唇能绕所述细腰部 转动。
  3. 如权利要求2所述的轴承，其特征在于，所述连接环包括沿轴承轴向延伸的第一悬空环、及连接所述抵挡环与所述第一悬空环的沿轴承径向延伸的过渡环，所述第一悬空环与抵挡环沿轴承径向间隔相对设置，所述根部固定在所述第一悬空环上。
  4. 如权利要求3所述的轴承，其特征在于，所述静密封环还包括自所述接触环的径向内周缘沿轴承轴向延伸并固设于内圈外周面上的固持环、及自所述接触环的径向外周缘沿轴承轴向延伸的第二悬空环，所述第二悬空环与所述固持环的延伸方向相反；
    所述第一悬空环、所述固持环沿轴承径向间隔相对设置并形成非接触式密封，所述抵挡环、所述第二悬空环沿轴承径向间隔相对设置并形成非接触式密封。
  5. 如权利要求4所述的轴承，其特征在于，所述弹性密封件的根部设有：位于所述第一悬空环与固持环之间的径向间隔内的第一迷宫密封环；
    所述密封结构还包括：第二迷宫密封环，位于所述抵挡环与第二悬空环之间的径向间隔内，并固定在所述第二悬空环上。
  6. 如权利要求1至5任一项所述的轴承，其特征在于，所述抵挡环靠近所述连接环的一端具有：自所述抵挡环轴向内端至轴向外端方向直径逐渐增大的锥形孔。
  7. 一种轴承，包括：转动的内圈；非转动的外圈；密封结构，位于所述内圈与外圈之间的径向间隙内，并在轴承的轴向端部密封轴 承；
    其特征在于，所述密封结构包括：同轴套设的静密封环和动密封环；
    所述静密封环固设于所述外圈内周面并包括沿轴承径向延伸的接触环；
    所述动密封环包括环形本体部和弹性密封件；
    所述本体部包括固设于内圈外周面上的连接环、及与所述连接环连接并位于所述连接环径向外侧的抵挡环，所述抵挡环沿轴承轴向延伸并与所述内圈存在径向间隔，所述抵挡环位于接触环的轴向外侧，所述连接环、抵挡环与所述接触环围成内腔，所述弹性密封件固设于所述连接环并包括突伸至所述内腔中的密封唇；
    在所述内圈的旋转速度小于临界值的条件下，所述弹性密封件的密封唇与所述接触环接触，并与所述抵挡环存在径向间隙；
    在所述内圈的旋转速度大于等于所述临界值的条件下，所述密封唇在离心力的作用下脱离所述接触环并抵靠所述抵挡环，使所述密封唇与所述静密封环形成非接触式密封。
  8. 如权利要求7所述的轴承，其特征在于，所述弹性密封件包括固定在所述连接环上的根部、及连接所述根部与密封唇的细腰部，所述细腰部的厚度小于所述密封唇的厚度，所述密封唇能绕所述细腰部转动。
  9. 如权利要求8所述的轴承，其特征在于，所述连接环包括沿轴承轴向延伸并固设于内圈外周面上的第一固持环、及连接所述第一固 持环与抵挡环的过渡环，所述第一固持环与抵挡环沿轴承径向相对设置，所述弹性密封件的根部固设于所述第一固持环上。
  10. 如权利要求9所述的轴承，其特征在于，所述静密封环还包括自所述接触环的径向外周缘沿轴承轴向延伸并固设于外圈内周面上的第二固持环、及自所述接触环的径向内周缘沿轴承轴向延伸的悬空环，所述悬空环与第二固持环的延伸方向相反；
    所述第一固持环、所述悬空环沿轴承径向间隔相对设置并形成非接触式密封，所述抵挡环、所述第二固持环沿轴承径向间隔相对设置并形成非接触式密封。
  11. 如权利要求10所述的轴承，其特征在于，所述密封结构还包括：第一迷宫密封环，位于所述第一固持环与悬空环之间的径向间隔内，并固定在所述悬空环上；
    第二迷宫密封环，位于所述抵挡环与第二固持环之间的径向间隔内，并固定在所述抵挡环上。
  12. 如权利要求7至11任一项所述的轴承，其特征在于，所述抵挡环具有：自所述抵挡环轴向内端至轴向外端方向直径逐渐减小的锥形孔。
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US9845827B2 (en) 2017-12-19
DE112015002746T5 (de) 2017-05-11
US20170152890A1 (en) 2017-06-01
CN105221580A (zh) 2016-01-06
CN105221580B (zh) 2019-01-18

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