JP6920174B2 - Sealed structure - Google Patents

Sealed structure Download PDF

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Publication number
JP6920174B2
JP6920174B2 JP2017215420A JP2017215420A JP6920174B2 JP 6920174 B2 JP6920174 B2 JP 6920174B2 JP 2017215420 A JP2017215420 A JP 2017215420A JP 2017215420 A JP2017215420 A JP 2017215420A JP 6920174 B2 JP6920174 B2 JP 6920174B2
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Prior art keywords
sealing
sealing surface
grease
contact
space
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JP2019086105A (en
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諭史 吉田
諭史 吉田
幸夫 井形
幸夫 井形
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JTEKT Corp
Koyo Sealing Techno Co Ltd
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JTEKT Corp
Koyo Sealing Techno Co Ltd
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Priority to JP2017215420A priority Critical patent/JP6920174B2/en
Priority to KR1020180134665A priority patent/KR102537909B1/en
Priority to DE102018127800.4A priority patent/DE102018127800A1/en
Priority to CN201811318260.8A priority patent/CN109751340B/en
Priority to TW107139447A priority patent/TWI763948B/en
Publication of JP2019086105A publication Critical patent/JP2019086105A/en
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    • 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
    • F16C33/723—Shaft end sealing means, e.g. cup-shaped caps or covers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • 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
    • 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
    • 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
    • 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
    • F16C33/7803—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings
    • F16C33/7809—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings for needle 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
    • F16C33/7826—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region of the opposing surface cooperating with the seal, e.g. a shoulder surface of a bearing ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7896—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members with two or more discrete sealings arranged in series
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
    • F16D3/38—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another
    • F16D3/382—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another constructional details of other than the intermediate member
    • F16D3/385—Bearing cup; Bearing construction; Bearing seal; Mounting of bearing on the intermediate member
    • 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
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3436—Pressing 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/41—Couplings

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing Of Bearings (AREA)
  • Sealing Devices (AREA)

Description

本発明は、例えば十字軸継手における軸部と軸受カップのように互いに相対回転する二つの部材の間に設けられる密封構造に関する。 The present invention relates to a sealing structure provided between two members that rotate relative to each other, such as a shaft portion and a bearing cup in a cross shaft joint.

例えば、鉄鋼用圧延機のスピンドル装置や自動車のドライブシャフトには、軸と軸との連結部にユニバーサルジョイントとして十字軸継手が用いられている。この十字軸継手は、４本の軸部を十字状に配置した十字軸と、各軸部に被せられる有底円筒状の軸受カップと、各軸部の外周面と軸受カップの内周面との間に転動自在に配設される複数の針状ころとを備え、軸受カップには各軸の端部に設けられたヨークが連結される。また、軸部と軸受カップとの間に形成される針状ころの収容空間への水等の浸入を防止し、当該収容空間から外部への潤滑剤の漏出を抑制するため、軸部の基端部と軸受カップの端部との間には、密封構造が設けられている（例えば、特許文献１参照）。 For example, in a spindle device of a rolling mill for steel and a drive shaft of an automobile, a cross shaft joint is used as a universal joint at a connecting portion between the shafts. This cross shaft joint includes a cross shaft in which four shaft portions are arranged in a cross shape, a bottomed cylindrical bearing cup that covers each shaft portion, an outer peripheral surface of each shaft portion, and an inner peripheral surface of the bearing cup. A plurality of needle-shaped rollers that are rotatably arranged between the bearing cups are provided, and a yoke provided at the end of each shaft is connected to the bearing cup. Further, in order to prevent water or the like from entering the accommodating space of the needle-shaped roller formed between the shaft portion and the bearing cup and to suppress the leakage of the lubricant from the accommodating space to the outside, the base of the shaft portion. A sealing structure is provided between the end portion and the end portion of the bearing cup (see, for example, Patent Document 1).

欧州特許公開１７８３３８４号European Patent Publication No. 1783384

本出願の発明者は、従前に図１１に示す密封構造を提案した（特願２０１６−２１７２９２号（未公開））。この密封構造は、軸受カップ１１１に取り付けられかつスリンガ１０６に摺接する環状のシール部材１０７を備え、スリンガ１０６が、径方向内側に向くシール面１４１を有し、シール部材７は、軸受カップ１１１に固定される芯金１３４と、芯金１３４に接着されシール面１４１に接触するリップ部１３１と、リップ部１３１をシール面４１側へ押圧するガータスプリング１５１と、を備えている。 The inventor of the present application has previously proposed the sealing structure shown in FIG. 11 (Japanese Patent Application No. 2016-217292 (unpublished)). This sealing structure includes an annular sealing member 107 that is attached to the bearing cup 111 and is in sliding contact with the slinger 106, the slinger 106 having a sealing surface 141 that faces inward in the radial direction, and the sealing member 7 on the bearing cup 111. It includes a core metal 134 to be fixed, a lip portion 131 that is adhered to the core metal 134 and comes into contact with the seal surface 141, and a garter spring 151 that presses the lip portion 131 toward the seal surface 41.

スリンガ１０６と軸受カップ１１１との間の空間（潤滑空間）をグリースで潤滑する場合、メンテナンスの際などに潤滑空間内のグリースを新しいグリースに入れ替えるには、新しいグリースを給脂孔から供給するに伴って、古いグリースをリップ部１３１から外部へ排出する必要がある。しかしながら、図１１に示す密封構造の場合、新たなグリースを潤滑空間に供給すると、図１２に矢印ｃで示すように、リップ部１３１をシール面１４１へ押し付ける力が作用し、シール面１４１に対向するリップ部１３１の側面１３１ｃ２の略全体がシール面１４１に強く接触する。そのため、リップ部１３１とシール面１４１との間を通して潤滑空間外部にグリースを排出することが困難となっていた。 When lubricating the space (lubrication space) between the slinger 106 and the bearing cup 111 with grease, to replace the grease in the lubrication space with new grease during maintenance, etc., supply new grease from the greasing holes. Along with this, it is necessary to discharge the old grease from the lip portion 131 to the outside. However, in the case of the sealing structure shown in FIG. 11, when new grease is supplied to the lubricating space, a force for pressing the lip portion 131 against the sealing surface 141 acts as shown by an arrow c in FIG. 12, and faces the sealing surface 141. Approximately the entire side surface 131c2 of the lip portion 131 is in strong contact with the sealing surface 141. Therefore, it is difficult to discharge the grease to the outside of the lubrication space through between the lip portion 131 and the sealing surface 141.

本発明は、グリースが充填される潤滑空間を密封する密封構造において、新たなグリースを供給する際の古いグリースの排出性能を高めることを目的とする。 An object of the present invention is to improve the discharge performance of old grease when supplying new grease in a sealed structure that seals a lubricating space filled with grease.

（１）本発明は、第１部材と、前記第１部材に径方向に対向して当該第１部材と同心状に配置され当該第１部材と相対回転する第２部材と、前記第１部材に取り付けられかつ前記第２部材に形成されたシール面に摺接する環状のシール部材と、を備え、前記第１部材と前記第２部材との間において、グリースが充填される潤滑空間を密封する密封構造であって、前記シール部材は、前記シール面に対向する対向面を有するリップ部と、前記対向面を前記シール面側へ押圧する押圧部材とを備え、前記リップ部は、前記対向面を有する接触部と、前記接触部を挟んで前記シール面とは反対側に位置する基部と、前記シール面に沿う方向における前記潤滑空間側の前記接触部の端部を、前記基部に接続する接続部とを有し、前記押圧部材が、前記接触部、基部、及び接続部で囲まれる空間に配置され、前記対向面は、前記シール面に沿う方向における前記潤滑空間の外部側において前記シール面に全周で接触する全接触領域と、前記潤滑空間にグリースを供給する際に、前記シール面に沿う方向における前記潤滑空間側において前記シール面に周方向に不連続に接触する部分接触領域とを有し、前記全接触領域は、前記潤滑空間にグリースを供給する際のグリースの供給圧によって前記シール面から押し上げられる。 (1) The present invention includes a first member, a second member that faces the first member in the radial direction and is arranged concentrically with the first member and rotates relative to the first member, and the first member. An annular sealing member that is attached to the second member and is in sliding contact with the sealing surface formed on the second member, and seals a lubrication space filled with grease between the first member and the second member. In a sealing structure, the sealing member includes a lip portion having a facing surface facing the sealing surface and a pressing member for pressing the facing surface toward the sealing surface side, and the lip portion is the facing surface. The contact portion having the and a connecting portion, the pressing member, the contact portion is disposed in a space surrounded by the base portion, and the connecting portion, the facing surface, the outside side of the lubricating space in the direction along the front Symbol sealing surface Partial contact between the entire contact area that contacts the seal surface all around and the seal surface that makes discontinuous contact with the seal surface on the lubrication space side in the direction along the seal surface when supplying grease to the lubrication space. possess a region, the total contact area is pushed up from the sealing surface by the supply pressure of the grease at the time of supplying the grease to the lubrication spaces.

上記構成によれば、潤滑空間内に供給されたグリースによってリップ部がシール面に押し付けられたとしても、対向面の部分接触領域では、シール面に接触していない部分が存在するため、当該部分に潤滑空間側からグリースが入り込み、そのグリースが全接触領域を押し上げて潤滑空間外部に排出される。したがって、新しいグリースを供給する際の古いグリースの排出性能を高めることができる。また、対向面が全接触領域を備えていることによって、第１の部分によるシール性は十分に確保することができる。 According to the above configuration, even if the lip portion is pressed against the sealing surface by the grease supplied into the lubrication space, there is a portion that is not in contact with the sealing surface in the partial contact region of the facing surface. Grease enters from the lubrication space side, and the grease pushes up the entire contact area and is discharged to the outside of the lubrication space. Therefore, it is possible to improve the discharge performance of the old grease when supplying the new grease. Further, since the facing surface includes the entire contact region, the sealing property of the first portion can be sufficiently ensured.

（２）好ましくは、前記全接触領域と前記部分接触領域との境界が、前記シール面に沿う方向における前記潤滑空間側に位置する前記押圧部材の端部よりも前記潤滑空間の外部側に配置されている。
このような構成によって、グリースの排出性能を高めることができる。 (2) Preferably, the boundary between the full contact region and the partial contact region is arranged on the outer side of the lubrication space from the end of the pressing member located on the lubrication space side in the direction along the sealing surface. Has been done.
With such a configuration, the grease discharge performance can be improved.

（３）好ましくは、前記境界が、前記シール面に沿う方向における前記押圧部材の中心よりも前記潤滑空間側に配置されている。
このような構成によって、全接触領域におけるシール性能を確保しつつグリースの排出性能も高めることができる。 (3) Preferably, the boundary is arranged on the lubrication space side with respect to the center of the pressing member in the direction along the sealing surface.
With such a configuration, it is possible to improve the grease discharge performance while ensuring the sealing performance in the entire contact region.

（４）好ましくは、前記対向面の部分接触領域には、前記シール面に沿う方向において前記潤滑空間側から前記潤滑空間の外部側へ向けて延びる溝が形成されている。
この構成によれば、潤滑空間内にグリースを供給する際に、潤滑空間内の古いグリースは、溝内に入り込んで全接触領域を押し上げ、潤滑空間の外部へ排出されるようになる。 (4) Preferably, a groove extending from the lubrication space side to the outside side of the lubrication space is formed in the partial contact region of the facing surface in the direction along the seal surface.
According to this configuration, when the grease is supplied into the lubrication space, the old grease in the lubrication space enters the groove, pushes up the entire contact area, and is discharged to the outside of the lubrication space.

（５）好ましくは、前記溝の横断面積が、前記シール面に沿う方向における前記潤滑空間側ほど大きい。
このような構成によって溝内にグリースが入り込みやすくなり、グリース供給の際に全接触領域を押し上げやすくして、グリースの排出を促進することができる。 (5) Preferably, the cross-sectional area of the groove is larger toward the lubrication space side in the direction along the sealing surface.
With such a configuration, it becomes easy for grease to enter the groove, and it becomes easy to push up the entire contact area when supplying grease, and it is possible to promote the discharge of grease.

（６）好ましくは、前記対向面の部分接触領域には、周方向に間隔をあけて複数の突起が形成されている。
このような突起を備えることによって、接触部の対向面とシール面との間に隙間を形成することができ、グリースを供給する際に、隙間にグリースを入り込ませて全接触領域を押し上げ、グリースを排出することができる。 (6) Preferably, a plurality of protrusions are formed at intervals in the circumferential direction in the partial contact region of the facing surface.
By providing such a protrusion, a gap can be formed between the facing surface of the contact portion and the sealing surface, and when the grease is supplied, the grease is allowed to enter the gap to push up the entire contact area, and the grease is supplied. Can be discharged.

（７）好ましくは、前記突起が、前記シール面に沿う方向における前記潤滑空間側に位置する前記押圧部材の端部よりも前記潤滑空間側に配置されている。
このような構成によって、接触部の潤滑空間側の端部を確実にシール面から浮かせて隙間を形成し、当該隙間にグリースを入り込ませることができる。 (7) Preferably, the protrusion is arranged on the lubrication space side of the end portion of the pressing member located on the lubrication space side in the direction along the seal surface.
With such a configuration, the end portion of the contact portion on the lubrication space side can be reliably lifted from the sealing surface to form a gap, and grease can be allowed to enter the gap.

本発明の密封構造によれば、グリースが充填される潤滑空間を密封する密封構造において、新たなグリースを供給する際の、古いグリースの排出性能を高めることができる。 According to the sealing structure of the present invention, in the sealing structure that seals the lubricating space filled with grease, it is possible to improve the discharge performance of old grease when supplying new grease.

第１の実施形態に係る密封構造を適用した十字軸継手の部分分解斜視図である。It is a partial decomposition perspective view of the cross shaft joint to which the sealing structure which concerns on 1st Embodiment is applied. 十字軸継手の側面図（一部断面図）である。It is a side view (partial sectional view) of a cross shaft joint. 密封構造の断面図である。It is sectional drawing of the sealed structure. 密封構造のシール部材の断面図である。It is sectional drawing of the sealing member of a sealing structure. シール部材の第１リップ部の作用を示す断面図である。It is sectional drawing which shows the action of the 1st lip part of a seal member. （ａ）は図５のＥ矢視図、（ｂ）は図５のＦ矢視図である。(A) is a view taken along the arrow E in FIG. 5, and (b) is a view taken along the line F in FIG. （ａ）は、グリースの供給圧が付与されていない第１リップ部を示す断面図、（ｂ）は、グリースの供給圧が付与されている第１リップ部を示す断面図である。(A) is a cross-sectional view showing a first lip portion to which a grease supply pressure is not applied, and (b) is a cross-sectional view showing a first lip portion to which a grease supply pressure is applied. 密封構造の第１シール面に対する全接触領域の面圧の変化を示す説明図である。It is explanatory drawing which shows the change of the surface pressure of the total contact area with respect to the 1st seal surface of a sealed structure. 第１リップ部の溝の変形例を示す図６に相当する図面である。It is a drawing corresponding to FIG. 6 which shows the modification of the groove of the 1st lip part. 第２の実施形態に係る密封構造の第１リップ部を拡大して示す断面図である。It is sectional drawing which shows the 1st lip part of the sealed structure which concerns on 2nd Embodiment enlarged. 従来技術に係る密封構造の断面図である。It is sectional drawing of the sealed structure which concerns on the prior art. 従来技術の密封構造において、グリースの供給圧が付与されているリップ部を示す断面図である。It is sectional drawing which shows the lip part which supply pressure of grease is applied in the sealing structure of the prior art.

以下、本発明の実施形態について図面を参照しながら説明する。
［第１の実施形態］
図１は、第１の実施形態に係る密封構造を適用した十字軸継手の部分分解斜視図、図２は、十字軸継手の側面図（一部断面図）である。
十字軸継手２０は、例えば鉄鋼用圧延機のスピンドル装置（図示省略）に用いられるものである。図１に示すように、十字軸継手２０は、４本の軸部４を有する十字軸２と、各軸部４に配設されたころ軸受部５と、一対のヨーク１７とを備えている。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[First Embodiment]
FIG. 1 is a partially disassembled perspective view of the cross shaft joint to which the sealing structure according to the first embodiment is applied, and FIG. 2 is a side view (partial cross-sectional view) of the cross shaft joint.
The cross-shaped joint 20 is used, for example, in a spindle device (not shown) of a rolling mill for steel. As shown in FIG. 1, the cross shaft joint 20 includes a cross shaft 2 having four shaft portions 4, a roller bearing portion 5 arranged on each shaft portion 4, and a pair of yokes 17. ..

十字軸２は、中央に設けられた基部３と、基部３から互いに直交する軸心Ｘ及び軸心Ｚに沿って四方向に延びる４本の軸部４とを有している。十字軸２は、基部３の中心を通過し、かつ、軸部４の軸心Ｘ及び軸心Ｚと直交する中心軸Ｃ回りに回転可能である。十字軸２には、ころ軸受部５の内部に潤滑剤を供給するための給脂路１３が軸心Ｘ及び軸心Ｚに沿って十字状に形成されている。 The cross axis 2 has a base portion 3 provided at the center, and four shaft portions 4 extending from the base portion 3 in four directions along an axis X and an axis Z orthogonal to each other. The cross axis 2 is rotatable around a central axis C that passes through the center of the base portion 3 and is orthogonal to the axial center X and the axial center Z of the shaft portion 4. In the cross shaft 2, a greasing passage 13 for supplying a lubricant to the inside of the roller bearing portion 5 is formed in a cross shape along the axis X and the axis Z.

図２に示すように、十字軸２の基部３の側面と、後述するころ軸受部５の軸受カップ１１とには、給脂路１３に接続される給脂孔３ａ，１１ａがそれぞれ形成されている。そして、ころ軸受部５内には、これらの給脂孔３ａ，１１ａ及び給脂路１３を介して潤滑剤が供給される。本実施形態では、潤滑剤としてグリースが使用される。また、グリースの供給は、十字軸継手２０を備えた装置の運転中に常時行われてもよいし、定期的（例えば、１〜３か月毎）に行われてもよい。 As shown in FIG. 2, greasing holes 3a and 11a connected to the greasing passage 13 are formed on the side surface of the base 3 of the cross shaft 2 and the bearing cup 11 of the roller bearing portion 5 described later, respectively. There is. Then, the lubricant is supplied into the roller bearing portion 5 through these greasing holes 3a and 11a and the greasing passage 13. In this embodiment, grease is used as the lubricant. Further, the grease may be supplied at all times during the operation of the device provided with the cross shaft joint 20, or may be performed at regular intervals (for example, every 1 to 3 months).

ころ軸受部５は、前述の軸部４と、複数の針状ころ９と、軸受カップ１１とを備えている。針状ころ９は、各軸部４の外周面に沿って転動自在に配置されている。軸受カップ１１は、有底筒状に形成されており、針状ころ９を介して軸部４の外周面に嵌合されている。したがって、針状ころ９は、軸受カップ１１の内周面を外輪軌道、軸部４の外周面を内輪軌道として転動し、これによって軸受カップ１１が軸部４の軸心Ｚ回りに揺動可能となっている。 The roller bearing portion 5 includes the shaft portion 4 described above, a plurality of needle-shaped rollers 9, and a bearing cup 11. The needle-shaped rollers 9 are rotatably arranged along the outer peripheral surface of each shaft portion 4. The bearing cup 11 is formed in a bottomed tubular shape, and is fitted to the outer peripheral surface of the shaft portion 4 via a needle-shaped roller 9. Therefore, the needle-shaped roller 9 rolls with the inner peripheral surface of the bearing cup 11 as the outer ring track and the outer peripheral surface of the shaft portion 4 as the inner ring track, whereby the bearing cup 11 swings around the axis Z of the shaft portion 4. It is possible.

軸部４の先端面と軸受カップ１１の底面との間には座金１０が設けられている。針状ころ９の軸心Ｚ方向内側には、ころガイド８、シール部材７及びスリンガ６が配設されている。シール部材７、スリンガ（第２部材）６、及び軸受カップ（第１部材）１１によって、本発明に係る密封構造１が構成されている。 A washer 10 is provided between the tip surface of the shaft portion 4 and the bottom surface of the bearing cup 11. A roller guide 8, a seal member 7, and a slinger 6 are arranged inside the needle-shaped roller 9 in the Z direction of the axis. The sealing structure 1 according to the present invention is composed of the sealing member 7, the slinger (second member) 6, and the bearing cup (first member) 11.

図３は、密封構造１の断面図である。図４は、スリンガ６に接触していない状態、すなわち自然状態のシール部材７を示す断面図である。
密封構造１は、軸部４と軸受カップ１１との間の針状ころ９が配置される空間であって潤滑剤としてのグリースが充填される潤滑空間内への水等の浸入を防止し、また、当該潤滑空間から外部への潤滑剤の漏出を防止するために設けられている。なお、本明細書では、図３における下側を「軸方向一方側」とし、上側を「軸方向他方側」としている。ただし、これらは軸方向における絶対的な特定の方向を指すものではなく、相対的な方向を指すものであるので、一方側と他方側とを入れ替えて読んでもよい。「径方向一方側」及び「径方向他方側」についても同様である。 FIG. 3 is a cross-sectional view of the sealed structure 1. FIG. 4 is a cross-sectional view showing a seal member 7 in a state where it is not in contact with the slinger 6, that is, in a natural state.
The sealing structure 1 prevents water or the like from entering the space in which the needle-shaped rollers 9 are arranged between the shaft portion 4 and the bearing cup 11 and is filled with grease as a lubricant. Further, it is provided to prevent leakage of the lubricant from the lubricating space to the outside. In this specification, the lower side in FIG. 3 is referred to as "one side in the axial direction", and the upper side is referred to as "the other side in the axial direction". However, since these do not refer to an absolute specific direction in the axial direction but to a relative direction, one side and the other side may be interchanged and read. The same applies to "one side in the radial direction" and "the other side in the radial direction".

密封構造１を構成するスリンガ６は環状に形成され、軸部４の基端部における外周面に嵌合されている。スリンガ６には、シール部材７におけるリップ部３１，３２，３３が接触するシール面４１，４２，４３が形成されている。また、スリンガ６は、軸部４の外周面に沿って筒形状に形成されたスリンガ本体６ａと、スリンガ本体６ａの軸方向一方側（図３の下側）において径方向外方へ延びる第１延長部６ｂと、第１延長部６ｂの先端側から軸方向他方側（図３の上側）に延びる第２延長部６ｃとを一体に有している。 The slinger 6 constituting the sealing structure 1 is formed in an annular shape and is fitted to the outer peripheral surface of the base end portion of the shaft portion 4. The slinger 6 is formed with sealing surfaces 41, 42, 43 that the lip portions 31, 32, 33 of the sealing member 7 come into contact with. Further, the slinger 6 is a first that extends outward in the radial direction on one side (lower side in FIG. 3) of the slinger main body 6a formed in a tubular shape along the outer peripheral surface of the shaft portion 4 in the axial direction. The extension portion 6b and the second extension portion 6c extending from the tip end side of the first extension portion 6b to the other side in the axial direction (upper side in FIG. 3) are integrally provided.

スリンガ本体６ａの外周面には、第２及び第３シール面４２，４３が軸方向に並べて形成されている。また、第２延長部６ｃの内周面には第１シール面４１が形成されている。この第１シール面４１は、軸方向に沿って形成されている。つまり、本実施形態においては、第１シール面４１に沿う方向と軸方向とが一致している。 The second and third sealing surfaces 42 and 43 are formed on the outer peripheral surface of the slinger main body 6a so as to be arranged in the axial direction. Further, a first seal surface 41 is formed on the inner peripheral surface of the second extension portion 6c. The first sealing surface 41 is formed along the axial direction. That is, in the present embodiment, the direction along the first sealing surface 41 and the axial direction coincide with each other.

なお、スリンガ６には、第２延長部６ｃからさらに径方向外側へ延びる第３延長部６ｄが設けられている。第２延長部６ｃの外周面及び第３延長部６ｄの軸方向他方側の側面は、それぞれ軸受カップ１１の端部に隙間をあけて対向している。この隙間は、スリンガ６と軸受カップ１１との間から水等が浸入するのを防止するシール隙間とされている。 The slinger 6 is provided with a third extension portion 6d extending radially outward from the second extension portion 6c. The outer peripheral surface of the second extension portion 6c and the side surface of the third extension portion 6d on the other side in the axial direction face each other with a gap at the end of the bearing cup 11. This gap is a seal gap that prevents water or the like from entering between the slinger 6 and the bearing cup 11.

シール部材７は、芯金（固定部）３４と、リップ部３１，３２，３３とを備えている。芯金３４は、軸受カップ１１の内周面に嵌合されることによって固定されている。芯金３４は、第１円筒部３４ａ１と、第１円筒部３４ａ１の軸方向他方側の端部から径方向内方へ屈曲する第１円環部３４ａ２とを有する第１芯金３４ａと、第２円筒部３４ｂ１と、第２円筒部３４ｂ１の軸方向一方側の端部から径方向内方へ屈曲する第２円環部３４ｂ２とを有する第２芯金３４ｂとからなる。第２円筒部３４ｂ１は、第１円筒部３４ａ１の径方向内側に重ね合わされ、第１円筒部３４ａ１の軸方向一方側の端部をカシメることによって、第２芯金３４ｂが第１芯金３４ａに固定されている。 The seal member 7 includes a core metal (fixing portion) 34 and lip portions 31, 32, 33. The core metal 34 is fixed by being fitted to the inner peripheral surface of the bearing cup 11. The core metal 34 includes a first core metal 34a having a first cylindrical portion 34a1 and a first annular portion 34a2 that bends inward in the radial direction from the end on the other side in the axial direction of the first cylindrical portion 34a1. It is composed of a second core metal 34b having two cylindrical portions 34b1 and a second annular portion 34b2 that bends inward in the radial direction from one end in the axial direction of the second cylindrical portion 34b1. The second cylindrical portion 34b1 is overlapped in the radial direction of the first cylindrical portion 34a1, and by caulking one end of the first cylindrical portion 34a1 in the axial direction, the second core metal 34b becomes the first core metal 34a. It is fixed to.

リップ部３１，３２，３３は、芯金３４に接着された第１リップ部３１、第２リップ部３２、及び第３リップ部３３からなる。第１リップ部３１及び第３リップ部３３は、第２芯金３４ｂの第２円環部３４ｂ２に接着され、第２リップ部３２は、第１芯金３４ａの第１円環部３４ａ２に接着されている。 The lip portions 31, 32, 33 are composed of a first lip portion 31, a second lip portion 32, and a third lip portion 33 adhered to the core metal 34. The first lip portion 31 and the third lip portion 33 are adhered to the second annular portion 34b2 of the second core metal 34b, and the second lip portion 32 is adhered to the first annular portion 34a2 of the first core metal 34a. Has been done.

第２リップ部３２は、第１円環部３４ａ２から軸方向一方側へ延伸している。第２リップ部３２の径方向内側の側面は、スリンガ６の第２シール面４２に接触する。第２リップ部３２の径方向外側の側面には、凹部３２ａが形成され、この凹部３２ａには、ガータスプリング（第２押圧部材）５２が設けられている。ガータスプリング５２は、コイルスプリングをリング状に形成したものであり、伸長する方向に弾性変形させた状態で第２リップ部３２の凹部３２ａに収容され、収縮する方向に弾性復帰することによって第２リップ部３２を第２シール面４２側へ押圧している。 The second lip portion 32 extends from the first annular portion 34a2 in one axial direction. The radial inner side surface of the second lip portion 32 comes into contact with the second sealing surface 42 of the slinger 6. A recess 32a is formed on the radial outer side surface of the second lip portion 32, and a garter spring (second pressing member) 52 is provided in the recess 32a. The garter spring 52 is a coil spring formed in a ring shape, and is housed in the recess 32a of the second lip portion 32 in a state of being elastically deformed in the extending direction, and elastically returns in the contracting direction to the second. The lip portion 32 is pressed toward the second sealing surface 42 side.

第３リップ部３３は、第２円環部３４ｂ２の径方向内側の端部から軸方向一方側へ延伸している。第３リップ部３３の径方向内側の側面は、スリンガ６の第３シール面４３に接触する。第３シール面４３は、軸方向一方側から他方側へ向けて徐々に外径が小さくなる傾斜面（円すい面）に形成されている。なお、この第３リップ部３３は、省略してもよい。また、本実施形態では、第３シール面４３が円錐形状に形成されているが、例えば、第３シール面４３は軸方向に平行な円筒面であってもよい。 The third lip portion 33 extends from the radially inner end of the second annulus portion 34b2 to one side in the axial direction. The radial inner side surface of the third lip portion 33 comes into contact with the third sealing surface 43 of the slinger 6. The third sealing surface 43 is formed on an inclined surface (conical surface) whose outer diameter gradually decreases from one side in the axial direction to the other side. The third lip portion 33 may be omitted. Further, in the present embodiment, the third sealing surface 43 is formed in a conical shape, but for example, the third sealing surface 43 may be a cylindrical surface parallel to the axial direction.

第１リップ部３１は、第２円環部３４ｂ２の軸方向一方側の側面から同方向へ延伸する基部（第１部分）３１ａと、基部３１ａの延伸端（軸方向一方側端部）から径方向外方へ延伸する接続部（第２部分）３１ｂと、接続部３１ｂの延伸端（径方向外端部）から軸方向他方側へ延伸する接触部（第３部分）３１ｃとを備えている。 The first lip portion 31 has a diameter from a base portion (first portion) 31a extending in the same direction from the side surface on one side in the axial direction of the second annular portion 34b2 and a diameter from the extending end (one side end portion in the axial direction) of the base portion 31a. It is provided with a connecting portion (second portion) 31b extending outward in the direction and a contact portion (third portion) 31c extending axially from the extending end (radial outer end portion) of the connecting portion 31b. ..

接触部３１ｃの径方向外側の側面（外周面）は、スリンガ６の第１シール面４１に対向する対向面３１ｃ２とされ、その少なくとも一部が第１シール面４１に接触する。
第１シール面４１を基準とすると、基部３１ａは、接触部３１ｃを挟んで第１シール面４１とは反対側に配置されている。また、接続部３１ｂは、基部３１ａと接触部３１ｃとの、第１シール面４１に沿う方向における潤滑空間側（軸方向一方側）の端部同士を接続している。 The radial outer side surface (outer peripheral surface) of the contact portion 31c is a facing surface 31c2 facing the first sealing surface 41 of the slinger 6, and at least a part thereof contacts the first sealing surface 41.
With the first seal surface 41 as a reference, the base portion 31a is arranged on the side opposite to the first seal surface 41 with the contact portion 31c interposed therebetween. Further, the connecting portion 31b connects the ends of the base portion 31a and the contact portion 31c on the lubrication space side (one side in the axial direction) in the direction along the first sealing surface 41.

基部３１ａと、接続部３１ｂと、接触部３１ｃとによって囲まれた空間（収容空間）Ｓには、ガータスプリング（第１押圧部材）５１が収容されている。また、基部３１ａと接触部３１ｃとの間には、ガータスプリング５１を収容空間Ｓに挿入するための開口Ａが形成されている。開口Ａは、軸方向他方側に開放している。ガータスプリング５１は、コイルスプリングをリング状に形成したものであり、収縮する方向に弾性変形させた状態で収容空間Ｓに収容され、伸張する方向に弾性復帰することにより接触部３１ｃを第１シール面４１側へ押圧するように構成されている。 A garter spring (first pressing member) 51 is accommodated in the space (accommodation space) S surrounded by the base portion 31a, the connecting portion 31b, and the contact portion 31c. Further, an opening A for inserting the garter spring 51 into the accommodation space S is formed between the base portion 31a and the contact portion 31c. The opening A is open to the other side in the axial direction. The garter spring 51 is formed by forming a coil spring in a ring shape, is accommodated in the accommodation space S in a state of being elastically deformed in the contracting direction, and elastically returns in the extending direction to seal the contact portion 31c first. It is configured to press toward the surface 41 side.

図５は、シール部材７の第１リップ部３１の作用を示す断面図である。
第１リップ部３１の接触部３１ｃは、図５に実線で示すように、スリンガ６の第１シール面４１に接触していない状態では、径方向外側に向けて傾斜している。この状態では、基部３１ａと接触部３１ｃとの間の開口Ａの幅Ｗ１は比較的広く形成されている。具体的には、開口Ａの一方の端縁である接触部３１ｃの先端内周縁（側縁）３１ｄの径方向位置ａは、ガータスプリング５１の径方向外端部の径方向位置ｂよりも径方向外側に配置されている。したがって、この開口Ａを介してガータスプリング５１を収容空間Ｓへ挿入しやすくなっている。 FIG. 5 is a cross-sectional view showing the action of the first lip portion 31 of the seal member 7.
As shown by the solid line in FIG. 5, the contact portion 31c of the first lip portion 31 is inclined outward in the radial direction when it is not in contact with the first seal surface 41 of the slinger 6. In this state, the width W1 of the opening A between the base portion 31a and the contact portion 31c is formed to be relatively wide. Specifically, the radial position a of the tip inner peripheral edge (side edge) 31d of the contact portion 31c, which is one end edge of the opening A, has a diameter larger than the radial position b of the radial outer end portion of the garter spring 51. It is located outside the direction. Therefore, the garter spring 51 can be easily inserted into the accommodation space S through the opening A.

一方、図５に二点鎖線で示すように、接触部３１ｃが第１シール面４１に当接している状態では、接触部３１ｃが径方向内方へ弾性変形し、基部３１ａとの間の開口Ａの幅Ｗ２が縮小されている。そして、接触部３１ｃの先端内周縁３１ｄにおける径方向位置ａ’は、ガータスプリング５１の径方向外端部の径方向位置ｂよりも径方向内側に配置されている。そのため、ガータスプリング５１が収容空間Ｓから離脱し難くなり、第１リップ部３１を第１シール面４１に確実に接触させることができる。特に、ガータスプリング５１は、収縮する方向に弾性変形されているので撓みやすくなり、収容空間Ｓから離脱しやすい状態となるが、開口Ａの幅を縮小することによってガータスプリング５１の離脱を確実に防止することができる。 On the other hand, as shown by the alternate long and short dash line in FIG. 5, when the contact portion 31c is in contact with the first sealing surface 41, the contact portion 31c is elastically deformed inward in the radial direction and the opening between the contact portion 31c and the base portion 31a is formed. The width W2 of A is reduced. The radial position a'on the inner peripheral edge 31d of the tip of the contact portion 31c is arranged radially inside the radial position b of the radial outer end portion of the garter spring 51. Therefore, the garter spring 51 is difficult to separate from the accommodation space S, and the first lip portion 31 can be surely brought into contact with the first sealing surface 41. In particular, since the garter spring 51 is elastically deformed in the contraction direction, it easily bends and easily separates from the accommodation space S. However, by reducing the width of the opening A, the garter spring 51 can be reliably separated. Can be prevented.

なお、第１リップ部３１における接触部３１ｃの先端内周縁３１ｄには、径方向内方へ膨出する膨出部３１ｃ１が形成されている。このような膨出部３１ｃ１を形成することによって、接触部３１ｃを第１シール面４１に接触させたときに、接触部３１ｃを径方向内側へ弾性変形させやすくしつつ、開口Ａの幅Ｗ２を可及的に小さくすることができる。 A bulging portion 31c1 that bulges inward in the radial direction is formed on the inner peripheral edge 31d of the tip of the contact portion 31c in the first lip portion 31. By forming such a bulging portion 31c1, when the contact portion 31c is brought into contact with the first sealing surface 41, the width W2 of the opening A is increased while making it easy for the contact portion 31c to be elastically deformed inward in the radial direction. It can be made as small as possible.

図３に示すように、本実施形態のシール部材７は、第１リップ部３１が径方向内側に向けて配置された第１シール面４１に接触し、第２リップ部３２及び第３リップ部３３が径方向外側に向けて配置された第２，第３シール面４２，４３に接触している。そのため、軸部４が軸受カップ１１に対して軸方向に移動したとしてもシール性が低下することがない。 As shown in FIG. 3, in the seal member 7 of the present embodiment, the first lip portion 31 comes into contact with the first seal surface 41 arranged so as to be radially inward, and the second lip portion 32 and the third lip portion 32 are in contact with each other. 33 is in contact with the second and third sealing surfaces 42 and 43 arranged so as to be radially outward. Therefore, even if the shaft portion 4 moves in the axial direction with respect to the bearing cup 11, the sealing property does not deteriorate.

また、軸部４が軸受カップ１１に対して径方向に移動した場合、軸部４の径方向の一方側では、第１リップ部３１が第１シール面４１から離れる方向に移動するが、第２，第３リップ部３２，３３は第２，第３シール面４２，４３に近づく方向へ移動し、径方向の他方側では、第２，第３リップ部３２，３３が第２，第３シール面４２，４３から離れる方向に移動するが、第１リップ部３１は第１シール面４１に近づく方向へ移動する。そのため、シール部材７の径方向の両側において略均一にシール性を確保することが可能となる。 Further, when the shaft portion 4 moves in the radial direction with respect to the bearing cup 11, the first lip portion 31 moves in the direction away from the first sealing surface 41 on one side of the shaft portion 4 in the radial direction. The second and third lip portions 32 and 33 move in the direction approaching the second and third sealing surfaces 42 and 43, and on the other side in the radial direction, the second and third lip portions 32 and 33 move to the second and third. The first lip portion 31 moves in a direction away from the sealing surfaces 42 and 43, but moves in a direction approaching the first sealing surface 41. Therefore, it is possible to ensure the sealing property substantially uniformly on both sides of the sealing member 7 in the radial direction.

スリンガ６は、第２，第３シール面４２，４３がスリンガ本体６ａの外周面に形成され、第２，第３シール面４２，４３よりも径方向外側に配置された第１シール面４１が第２延長部６ｃの内周面に形成されている。したがって、第２、第３シール面４２，４３と第１シール面４１とは、互いに径方向に間隔をあけて対向した配置となり、両者の間には、シール部材７を配置するためのスペースが形成されている。当該スペースにシール部材７を挿入することによって、径方向に関して互いに逆向きに配置された第１シール面４１及び第２，第３シール面４２，４３にリップ部３１〜３３を接触させることができる。また、第１シール面４１と第３シール面４３とは、軸方向に関して重複した位置に配置されているので密封構造１の軸方向の寸法を可及的に小さくすることができる。 In the slinger 6, the second and third sealing surfaces 42 and 43 are formed on the outer peripheral surface of the slinger main body 6a, and the first sealing surface 41 arranged radially outside the second and third sealing surfaces 42 and 43 is formed. It is formed on the inner peripheral surface of the second extension portion 6c. Therefore, the second and third seal surfaces 42 and 43 and the first seal surface 41 are arranged so as to face each other with a radial distance from each other, and there is a space between them for arranging the seal member 7. It is formed. By inserting the seal member 7 into the space, the lip portions 31 to 33 can be brought into contact with the first seal surface 41 and the second and third seal surfaces 42, 43 arranged in opposite directions with respect to the radial direction. .. Further, since the first sealing surface 41 and the third sealing surface 43 are arranged at overlapping positions with respect to the axial direction, the axial dimension of the sealing structure 1 can be reduced as much as possible.

前述したように、本実施形態の密封構造１は、グリース潤滑されるころ軸受部５の内部空間（潤滑空間）を密封する。以下、図３に示すように、第１シール面４１に沿う方向（軸方向）に関して、第１リップ部３１よりもころ軸受部５の内部側を「潤滑空間側」ともいい、第１リップ部３１よりも外側を「潤滑空間外部側」ともいう。 As described above, the sealing structure 1 of the present embodiment seals the internal space (lubricating space) of the roller bearing portion 5 to be grease-lubricated. Hereinafter, as shown in FIG. 3, with respect to the direction (axial direction) along the first sealing surface 41, the inner side of the roller bearing portion 5 with respect to the first lip portion 31 is also referred to as the “lubrication space side”, and the first lip portion. The outside of 31 is also referred to as the "outside side of the lubrication space".

図５に示すように、第１リップ部３１における接触部３１ｃは、第１シール面４１に対向する側面（以下、「対向面」ともいう）３１ｃ２を有し、この対向面３１ｃ２には、溝６１が形成されている。この溝６１は、接触部３１ｃの潤滑空間側の端部から潤滑空間外部側へ向けて軸方向に延びている。また、図６に示すように、溝６１は、第１リップ部３１の周方向に間隔をあけて複数箇所に形成されている。例えば、溝６１は、周方向に等間隔で１６個所に形成されている。本実施形態の溝６１の底面の横断面（軸心に直交する方向の断面）は、略円弧状に形成されている。 As shown in FIG. 5, the contact portion 31c in the first lip portion 31 has a side surface (hereinafter, also referred to as “opposing surface”) 31c2 facing the first seal surface 41, and the facing surface 31c2 has a groove. 61 is formed. The groove 61 extends axially from the end of the contact portion 31c on the lubrication space side toward the outside of the lubrication space. Further, as shown in FIG. 6, the grooves 61 are formed at a plurality of locations at intervals in the circumferential direction of the first lip portion 31. For example, the grooves 61 are formed at 16 positions at equal intervals in the circumferential direction. The cross section of the bottom surface of the groove 61 of the present embodiment (cross section in the direction orthogonal to the axis) is formed in a substantially arc shape.

また、溝６１は、潤滑空間側の深溝部６１ａと、潤滑空間外部側の浅溝部６１ｂとを備える。深溝部６１ａ及び浅溝部６１ｂは、ともに軸方向に関して潤滑空間側が深くなるように底面が第１シール面４１に対して傾斜している。また、深溝部６１ａの底面の傾斜は、浅溝部６１ｂの底面の傾斜よりも急となっている。図６に示すように、深溝部６１ａと浅溝部６１ｂの周方向の幅Ｗ３は略同一とされている。以上より、溝６１は、潤滑空間側において横断面積がより大きく、潤滑空間外部側において横断面積がより小さくなっている。 Further, the groove 61 includes a deep groove portion 61a on the lubrication space side and a shallow groove portion 61b on the outer side of the lubrication space. The bottom surface of both the deep groove portion 61a and the shallow groove portion 61b is inclined with respect to the first sealing surface 41 so that the lubrication space side becomes deeper in the axial direction. Further, the inclination of the bottom surface of the deep groove portion 61a is steeper than the inclination of the bottom surface of the shallow groove portion 61b. As shown in FIG. 6, the width W3 of the deep groove portion 61a and the shallow groove portion 61b in the circumferential direction is substantially the same. From the above, the groove 61 has a larger cross-sectional area on the lubrication space side and a smaller cross-sectional area on the outer side of the lubrication space.

図７（ａ）は、第１シール面４１に接触した第１リップ部３１の接触部３１ｃを示している。この状態で、接触部３１ｃの対向面３１ｃ２は、その軸方向他方側（潤滑空間外部側）の一部が第１シール面４１に接触し、軸方向一方側（潤滑空間側）の一部が第１シール面４１から隙間ｓをあけて僅かに浮いた状態となっている。 FIG. 7A shows the contact portion 31c of the first lip portion 31 in contact with the first seal surface 41. In this state, a part of the facing surface 31c2 of the contact portion 31c is in contact with the first sealing surface 41 on the other side in the axial direction (outside the lubrication space side), and a part on the one side in the axial direction (on the lubrication space side). It is in a state of being slightly floated with a gap s from the first sealing surface 41.

図７（ｂ）は、さらに潤滑空間にグリースを供給しているときの第１リップ部３１を示す。潤滑空間にグリースが供給されると、当該グリースの供給圧によって第１リップ部３１が矢印ｃ方向に押圧されるため、接触部３１ｃの対向面３１ｃ２のうち、第１シール面４１から浮いていた部分が第１シール面４１に接触する。 FIG. 7B shows the first lip portion 31 when grease is further supplied to the lubrication space. When grease is supplied to the lubrication space, the first lip portion 31 is pressed in the direction of arrow c by the supply pressure of the grease, so that the first lip portion 31 floats from the first seal surface 41 of the facing surfaces 31c2 of the contact portion 31c. The portion comes into contact with the first sealing surface 41.

このとき、図６（ｂ）にも示すように、接触部３１ｃの対向面３１ｃ２は、溝６１の軸方向一方側（潤滑空間外部側）の端部の位置Ｌよりも軸方向一方側の領域が、第１シール面４１に対して全周（全面）で接触する全接触領域Ｒ１となっている。また、溝６１の軸方向一方側の端部の位置Ｌよりも軸方向他方側の領域が、溝６１を除いて第１シール面４１に周方向に不連続（断続的）に接触する部分接触領域Ｒ２となっている。つまり、接触部３１ｃの対向面３１ｃ２は、全接触領域Ｒ１と部分接触領域Ｒ２とを有している。 At this time, as shown in FIG. 6B, the facing surface 31c2 of the contact portion 31c is a region on one side in the axial direction from the position L of the end portion on one side in the axial direction (outside side of the lubrication space) of the groove 61. However, the entire contact region R1 is in contact with the first seal surface 41 on the entire circumference (entire surface). Further, the region on the other side in the axial direction from the position L of the end portion on one side in the axial direction of the groove 61 makes partial contact (intermittently) with the first sealing surface 41 in the circumferential direction except for the groove 61. It is the area R2. That is, the facing surface 31c2 of the contact portion 31c has a full contact region R1 and a partial contact region R2.

したがって、図７（ｂ）に示すように第１リップ部３１がグリースによって矢印ｃ方向に押圧されたとしても、部分接触領域Ｒ２の溝６１は第１シール面４１に接触しない。そのため、潤滑空間内のグリースは、溝６１に入り込むとともに、供給圧によって接触部３１ｃを押し上げ、接触部３１ｃの全接触領域Ｒ１と第１シール面４１との間から排出される（矢印ｄ参照）。したがって、潤滑空間内で新しいグリースと古いグリースとの入れ替えを好適に行うことができる。 Therefore, as shown in FIG. 7B, even if the first lip portion 31 is pressed by the grease in the direction of arrow c, the groove 61 of the partial contact region R2 does not come into contact with the first sealing surface 41. Therefore, the grease in the lubricating space enters the groove 61, pushes up the contact portion 31c by the supply pressure, and is discharged from between the entire contact region R1 of the contact portion 31c and the first sealing surface 41 (see arrow d). .. Therefore, the new grease and the old grease can be preferably replaced in the lubrication space.

図６（ａ）に示すように、溝６１は、潤滑空間側の横断面積が潤滑空間外部側の横断面積よりも広いため、溝６１内へグリースが流入し易くなり、グリース供給時のグリースの排出性能をより高めることができる。 As shown in FIG. 6A, since the cross-sectional area on the lubrication space side of the groove 61 is wider than the cross-sectional area on the outer side of the lubrication space, grease easily flows into the groove 61, and the grease when the grease is supplied The discharge performance can be further improved.

図７（ｂ）に示すように、接触部３１ｃの対向面３１ｃ２において、全接触領域Ｒ１と部分接触領域Ｒ２との境界Ｌは、ガータスプリング５１の軸方向一方側（潤滑空間側）の端部５１ｂと、ガータスプリング５１の中心５１ａとの間の軸方向の範囲Ｄ１に位置している。境界Ｌが、端部５１ｂよりも軸方向一方側に配置されていると、溝６１内に入り込んだグリースによって対向面３１ｃ２の全接触領域Ｒ１を押し上げることが困難となり、境界Ｌが、中心５１ａよりも軸方向他方側（潤滑空間外部側）に配置されていると、全接触領域Ｒ１の面圧の関係より、接触部３１ｃによるシール性能が低下するからである。 As shown in FIG. 7B, on the facing surface 31c2 of the contact portion 31c, the boundary L between the full contact region R1 and the partial contact region R2 is the end portion of the garter spring 51 on one axial side (lubrication space side). It is located in the axial range D1 between the 51b and the center 51a of the garter spring 51. If the boundary L is arranged on one side in the axial direction from the end portion 51b, it becomes difficult for the grease that has entered the groove 61 to push up the entire contact region R1 of the facing surface 31c2, and the boundary L is located on the center 51a. This is because if it is arranged on the other side in the axial direction (outside the lubrication space), the sealing performance by the contact portion 31c deteriorates due to the relationship of the surface pressure of the entire contact region R1.

図８は、グリースの供給圧が第１リップ部３１に作用しているときの、第１シール面４１に対する全接触領域Ｒ１の面圧の変化を示す。
図８（ａ）に示すように、全接触領域Ｒ１と部分接触領域Ｒ２との境界Ｌが、ガータスプリング５１の中心５１ａと一致している場合、第１シール面４１に対する全接触領域Ｒ１の面圧が、潤滑空間側の端部でピーク（点Ｐ１参照）となる。そのため、潤滑空間外部側から水等が浸入しやすくなる。 FIG. 8 shows the change in the surface pressure of the total contact region R1 with respect to the first sealing surface 41 when the grease supply pressure acts on the first lip portion 31.
As shown in FIG. 8A, when the boundary L between the total contact area R1 and the partial contact area R2 coincides with the center 51a of the garter spring 51, the surface of the total contact area R1 with respect to the first sealing surface 41. The pressure peaks at the end on the lubrication space side (see point P1). Therefore, water or the like easily infiltrates from the outside of the lubrication space.

図８（ｂ）に示すように、境界Ｌが、ガータスプリング５１の中心５１ａよりも潤滑空間側にある場合、第１シール面４１に対する全接触領域Ｒ１の面圧が、潤滑空間外部側の端部でピーク（点Ｐ２参照）となっている。そのため、潤滑空間外部側からの水等の浸入を好適に防止することができ、シール性能を好適に維持することができる。 As shown in FIG. 8B, when the boundary L is on the lubrication space side of the center 51a of the garter spring 51, the surface pressure of the entire contact region R1 with respect to the first sealing surface 41 is the end on the outer side of the lubrication space. There is a peak in the section (see point P2). Therefore, it is possible to suitably prevent the intrusion of water or the like from the outside of the lubrication space, and it is possible to preferably maintain the sealing performance.

図９は、第１リップ部３１の溝６１の変形例を示す図６に相当する図面である。
この変形例に係る溝６１は、深溝部６１ａの周方向の幅Ｗ４が、浅溝部６１ｂの幅Ｗ３よりも大きく形成されている。深溝部６１ａの横断面形状は略円弧状に形成されている。本変形例によれば、深溝部６１ａにおける横断面形状をより大きくすることができ、溝６１内へのグリースの流入をより促進することができる。 FIG. 9 is a drawing corresponding to FIG. 6 showing a modified example of the groove 61 of the first lip portion 31.
In the groove 61 according to this modification, the width W4 of the deep groove portion 61a in the circumferential direction is formed to be larger than the width W3 of the shallow groove portion 61b. The cross-sectional shape of the deep groove portion 61a is formed in a substantially arc shape. According to this modification, the cross-sectional shape of the deep groove portion 61a can be made larger, and the inflow of grease into the groove 61 can be further promoted.

［第２の実施形態］
図１０は、第２の実施形態に係る密封構造の第１リップ部を拡大して示す断面図である。
本実施形態では、接触部３１ｃの対向面３１ｃ２に、溝６１に代えて突起６２が周方向に間隔をあけて複数個所に設けられている。この突起６２は、ガータスプリング５１の軸方向一方側（潤滑空間側）の端部５１ｂよりも、さらに軸方向一方側の範囲Ｄ２に配置されている。 [Second Embodiment]
FIG. 10 is an enlarged cross-sectional view showing a first lip portion of the sealed structure according to the second embodiment.
In the present embodiment, protrusions 62 are provided at a plurality of positions on the facing surface 31c2 of the contact portion 31c at intervals in the circumferential direction instead of the grooves 61. The protrusion 62 is arranged in the range D2 on one side in the axial direction, rather than the end portion 51b on one side in the axial direction (lubrication space side) of the garter spring 51.

このような突起６２を備えることによって、潤滑空間内にグリースを供給したときに、グリースの供給圧によって対向面３１ｃ２全体が第１シール面４１に接触することはなく、対向面３１ｃ２と第１シール面４１との間には常時隙間ｓが形成される。そのため、当該隙間ｓにグリースが入り込み、入り込んだグリースが接触部３１ｃの全接触領域Ｒ１を押し上げることによってグリースを排出することができる。 By providing such a protrusion 62, when grease is supplied into the lubrication space, the entire facing surface 31c2 does not come into contact with the first sealing surface 41 due to the supply pressure of the grease, and the facing surface 31c2 and the first seal are provided. A gap s is always formed between the surface 41 and the surface 41. Therefore, the grease enters the gap s, and the entered grease pushes up the entire contact region R1 of the contact portion 31c, so that the grease can be discharged.

また、範囲Ｄ２に突起６２が形成されることによって、接触部３１ｃの潤滑空間側の端部を確実に第１シール面４１から浮かせて隙間ｓを形成し、グリースを入り込ませることができる。 Further, by forming the protrusion 62 in the range D2, the end portion of the contact portion 31c on the lubrication space side can be reliably lifted from the first sealing surface 41 to form a gap s, and grease can be introduced.

本発明は、上記の実施形態に限定されることなく特許請求の範囲に記載された発明の範囲内において変更することが可能である。
例えば、第１リップ部３１の接触部３１ｃに形成される溝６１及び突起６２の個数、軸方向の長さ、周方向の幅、横断面形状等は、適宜変更することができる。 The present invention is not limited to the above embodiments and can be modified within the scope of the invention described in the claims.
For example, the number of grooves 61 and protrusions 62 formed in the contact portion 31c of the first lip portion 31, the length in the axial direction, the width in the circumferential direction, the cross-sectional shape, and the like can be appropriately changed.

シール部材７は、スリンガ６ではなく軸部４に直接接触するものであってもよい。また、シール部材７は、軸部４側に固定され、軸受カップ１１側に接触するように構成されていてもよい。
本発明の密封構造１は、十字軸継手２０における軸部４と軸受カップ１１との間以外にも適用可能である。 The seal member 7 may be in direct contact with the shaft portion 4 instead of the slinger 6. Further, the seal member 7 may be fixed to the shaft portion 4 side and may be configured to come into contact with the bearing cup 11 side.
The sealing structure 1 of the present invention can be applied to other than between the shaft portion 4 and the bearing cup 11 in the cross shaft joint 20.

１：密封構造、６：スリンガ（第１部材）、７：シール部材、１１：軸受カップ（第２部材）、２０：十字軸継手、３１：第１リップ部、３１ａ：基部、３１ｂ：接続部、３１ｃ：接触部、３１ｃ２：対向面、４１：第１シール面、５１：ガータスプリング（押圧部材）、５１ａ：中心、５１ｂ：端部、６１：溝、６１ａ：深溝部、６１ｂ：浅溝部、６２：突起 1: Sealed structure, 6: Slinger (1st member), 7: Sealing member, 11: Bearing cup (2nd member), 20: Cross shaft joint, 31: 1st lip part, 31a: Base part, 31b: Connection part , 31c: contact part, 31c2: facing surface, 41: first seal surface, 51: garter spring (pressing member), 51a: center, 51b: end part, 61: groove, 61a: deep groove part, 61b: shallow groove part, 62: Protrusion

Claims (7)

第１部材と、前記第１部材に径方向に対向して当該第１部材と同心状に配置され当該第１部材と相対回転する第２部材と、前記第１部材に取り付けられかつ前記第２部材に形成されたシール面に摺接する環状のシール部材と、を備え、前記第１部材と前記第２部材との間において、グリースが充填される潤滑空間を密封する密封構造であって、
前記シール部材は、前記シール面に対向する対向面を有するリップ部と、前記対向面を前記シール面側へ押圧する押圧部材と、を備え、
前記リップ部は、前記対向面を有する接触部と、前記接触部を挟んで前記シール面とは反対側に位置する基部と、前記シール面に沿う方向における前記潤滑空間側の前記接触部の端部を、前記基部に接続する接続部とを有し、
前記押圧部材が、前記接触部、基部、及び接続部で囲まれる空間に配置され、
前記対向面は、前記シール面に沿う方向における前記潤滑空間の外部側において前記シール面に全周で接触する全接触領域と、前記潤滑空間にグリースを供給する際に、前記シール面に沿う方向における前記潤滑空間側において前記シール面に周方向に不連続に接触する部分接触領域とを有し、
前記全接触領域は、前記潤滑空間にグリースを供給する際のグリースの供給圧によって前記シール面から押し上げられる、密封構造。 A first member, a second member that is arranged concentrically with the first member in a radial direction and rotates relative to the first member, and a second member that is attached to the first member and that is attached to the first member. It is a sealing structure including an annular sealing member that is slidably contacted with a sealing surface formed on the member, and seals a lubricating space filled with grease between the first member and the second member.
The sealing member includes a lip portion having a facing surface facing the sealing surface, and a pressing member for pressing the facing surface toward the sealing surface.
The lip portion includes a contact portion having the facing surface, a base portion located on the opposite side of the contact portion from the sealing surface, and an end of the contact portion on the lubrication space side in a direction along the sealing surface. The unit has a connection portion that connects the portion to the base portion, and has a connection portion.
The pressing member is arranged in a space surrounded by the contact portion, the base portion, and the connection portion.
The facing surface, and the total contact area of the outer side of the lubricating space in the direction along the front Symbol sealing surface in contact with the entire circumference on the sealing surface, when supplying grease to the lubrication spaces, along the sealing surface possess a partial contact area discontinuously contacts the circumferential direction on the seal surface in the lubricant space side in the direction,
The entire contact area has a sealed structure in which the grease is pushed up from the sealing surface by the supply pressure of the grease when the grease is supplied to the lubricating space. 前記全接触領域と前記部分接触領域との境界が、前記シール面に沿う方向における前記潤滑空間側に位置する前記押圧部材の端部よりも前記潤滑空間の外部側に配置されている、請求項１に記載の密封構造。 A claim that the boundary between the full contact region and the partial contact region is arranged on the outer side of the lubrication space from the end of the pressing member located on the lubrication space side in the direction along the sealing surface. The sealed structure according to 1. 前記境界が、前記シール面に沿う方向における前記押圧部材の中心よりも前記潤滑空間側に配置されている、請求項２に記載の密封構造。 The sealing structure according to claim 2, wherein the boundary is arranged on the lubricating space side with respect to the center of the pressing member in the direction along the sealing surface. 前記対向面の部分接触領域には、前記シール面に沿う方向において前記潤滑空間側から前記潤滑空間の外部側へ向けて延びる溝が形成されている、請求項１〜３のいずれか１項に記載の密封構造。 3. The sealed structure described. 前記溝の横断面積が、前記シール面に沿う方向における前記潤滑空間側ほど大きい、請求項４に記載の密封構造。 The sealing structure according to claim 4, wherein the cross-sectional area of the groove is larger toward the lubricating space side in the direction along the sealing surface. 前記対向面の部分接触領域には、周方向に間隔をあけて複数の突起が形成されている、請求項１〜３のいずれか１項に記載の密封構造。 The sealing structure according to any one of claims 1 to 3, wherein a plurality of protrusions are formed at intervals in the circumferential direction in the partial contact region of the facing surface. 前記突起が、前記シール面に沿う方向における前記潤滑空間側に位置する前記押圧部材の端部よりも前記潤滑空間側に配置されている、請求項６に記載の密封構造。 The sealing structure according to claim 6, wherein the protrusions are arranged on the lubricating space side with respect to the end portion of the pressing member located on the lubricating space side in the direction along the sealing surface.
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KR1020180134665A KR102537909B1 (en) 2017-11-08 2018-11-05 Sealing structure
DE102018127800.4A DE102018127800A1 (en) 2017-11-08 2018-11-07 sealing structure
CN201811318260.8A CN109751340B (en) 2017-11-08 2018-11-07 Sealing structure
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JP2002031243A (en) * 2000-07-17 2002-01-31 Koyo Seiko Co Ltd Bearing sealing device for cross coupling
DE102005053558A1 (en) * 2005-11-08 2007-05-24 Voith Turbo Gmbh & Co. Kg Gimbal assembly
EP1969261A1 (en) 2006-01-05 2008-09-17 Saint-Gobain Performance Plastics Corporation Annular seal and pump including same
JP2008144784A (en) * 2006-12-06 2008-06-26 Nok Corp Packing and sealing system
JP5760265B2 (en) 2011-05-25 2015-08-05 株式会社アドヴィックス Annular seal member
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