JP5577032B2

JP5577032B2 - Seal structure

Info

Publication number: JP5577032B2
Application number: JP2008309797A
Authority: JP
Inventors: 一彦末岡; 健天沼
Original assignee: Fukoku Co Ltd
Current assignee: Fukoku Co Ltd
Priority date: 2008-12-04
Filing date: 2008-12-04
Publication date: 2014-08-20
Anticipated expiration: 2028-12-04
Also published as: JP2010133487A; WO2010064690A1

Description

本発明は、シール構造に関し、特に、等速ジョイント用樹脂製ブーツと等速ジョイントのシャフト又はアウターケースとの間のシール性の向上を図るためのシール構造に関するものである。 The present invention relates to a seal structure, and more particularly to a seal structure for improving the sealing performance between a resin boot for a constant velocity joint and the shaft or outer case of the constant velocity joint.

従来より、例えば自動車の駆動軸（ドライブシャフト）や推進軸（プロペラシャフト）に用いられる等速ジョイントには、潤滑剤としてのグリースを密封すると共に、外部からの塵や水などの浸入を防ぐための樹脂製ブーツを装着したものが実用化されており、そのシール性を維持するためのシール構造が種々検討されている。一例として、特許文献１には、等速ジョイントのシャフトに締結させる小径筒部を有する樹脂製ブーツが開示されており、この樹脂製ブーツの小径筒部には、締結バンド等の締結部材によって締め付ける内周側領域に樹脂製のシール部が構成されていると共に、当該シール部の内周面に樹脂製のリップが周方向に沿って連続して突設されている。 Conventionally, for example, constant velocity joints used for driving shafts (propeller shafts) and propulsion shafts (propeller shafts) of automobiles are sealed with grease as a lubricant and prevented from entering dust and water from the outside. Those equipped with the above-mentioned resin boots have been put into practical use, and various seal structures for maintaining the sealing performance have been studied. As an example, Patent Literature 1 discloses a resin boot having a small-diameter cylindrical portion that is fastened to a shaft of a constant velocity joint, and the small-diameter cylindrical portion of the resin boot is fastened by a fastening member such as a fastening band. A resin seal portion is formed in the inner peripheral region, and a resin lip is continuously provided along the circumferential direction on the inner peripheral surface of the seal portion.

このような小径筒部を締結部材で締め付けると、そのときの締付力によってシール部が潰れてシャフトに圧接すると共に、リップの先端がシャフトに形成されたリップ溝に押し付けられて圧接する。これにより、当該ブーツとシャフトとのシール性が維持されている。
特開２００４−２９１４３８号公報 When such a small-diameter cylindrical portion is tightened with a fastening member, the sealing portion is crushed and pressed against the shaft by the tightening force at that time, and the tip of the lip is pressed against the lip groove formed on the shaft to be pressed. Thereby, the sealing performance between the boot and the shaft is maintained.
JP 2004-291438 A

ところで、上記したようなリップや突起等の突状シールを締結部材の締付力によって潰し、その先端部をシャフトに圧接させるシール構造では、突状シールは、先端側から根元側に向けて圧潰した状態でシャフトに圧接しているため、その全体が圧縮変形し、シャフトに対して隙間無く圧接した状態となっている。そして、この状態でシャフトに締結されたブーツが、特に、インボード側のブーツである場合には、高温（エンジン駆動時の雰囲気温度）と低温（エンジン停止時の雰囲気温度）とが繰り返される雰囲気中で使用される。 By the way, in the seal structure in which the projecting seal such as the lip and the projection as described above is crushed by the tightening force of the fastening member and its tip is pressed against the shaft, the projecting seal is crushed from the tip side toward the root side. In this state, the shaft is pressed against the shaft, so that the whole is compressed and deformed, and is pressed against the shaft without any gap. When the boot fastened to the shaft in this state is an inboard side boot, in particular, an atmosphere in which high temperature (atmospheric temperature when the engine is driven) and low temperature (atmospheric temperature when the engine is stopped) is repeated. Used in.

ここで、上記したようなブーツとシャフトとを高温の雰囲気中で使用すると、締結部材の締結力によって圧縮変形している突状シールの弾性復元力が低下する現象（所謂ヘタリ）が生じる場合がある。
具体的に説明すると、高温の雰囲気中では、締結部材を含めてブーツ全体が熱膨張するが、突状シールは樹脂製であるため、その膨張量は金属製の締結部材よりも大きなものとなる。このとき、突状シールは、締結部材による一定の締付力でシャフトに対して隙間無く圧接した状態となっているため、高温雰囲気下での熱膨張が強制的に制限されてしまう。この結果、締結部材の締結力によって圧縮変形している突状シールの弾性復元力が低下する現象（所謂ヘタリ）が生じることになる。 Here, when the boot and the shaft as described above are used in a high-temperature atmosphere, a phenomenon (so-called “sagging”) in which the elastic restoring force of the projecting seal that is compressively deformed by the fastening force of the fastening member may occur. is there.
Specifically, in a high temperature atmosphere, the entire boot including the fastening member is thermally expanded. However, since the projecting seal is made of resin, the expansion amount is larger than that of the metal fastening member. . At this time, since the projecting seal is in a state of being pressed against the shaft without a gap with a constant tightening force by the fastening member, thermal expansion in a high temperature atmosphere is forcibly limited. As a result, a phenomenon in which the elastic restoring force of the projecting seal that is compressively deformed by the fastening force of the fastening member is reduced (so-called sag) occurs.

このように、突状シールに「ヘタリ」が生じると、シャフトに対する突状シールの面圧（圧接力）が低下する。さらに、雰囲気温度が高温（エンジン駆動時）から低温（エンジン停止時）に低下した場合には、突状シールもこの温度低下によって収縮するが、突状シールに「ヘタリ」が生じていると、突状シールの面圧（圧接力）が低下した状態で突状シールも収縮するため、シャフトに対する突状シールの面圧（圧接力）がさらに低下し、或いは、突状シールの先端とシャフトとの間に隙間が生じてしまう場合もある。そうなると、上記した圧接力の低下の程度や隙間の大きさの程度によっては、ブーツとシャフトとの間のシール性を長期に亘って一定に維持することが困難となり、その結果、早期にグリース洩れが発生したり、外部から塵や水などが浸入したりする虞がある。 As described above, when “sticky” occurs in the projecting seal, the surface pressure (pressure contact force) of the projecting seal with respect to the shaft decreases. Furthermore, when the ambient temperature decreases from a high temperature (when the engine is driven) to a low temperature (when the engine is stopped), the projecting seal also contracts due to this temperature decrease. Since the projecting seal contracts in a state where the surface pressure (pressure contact force) of the projecting seal is reduced, the surface pressure (pressure contact force) of the projecting seal against the shaft further decreases, or the tip of the projecting seal and the shaft There may be a gap between the two. As a result, depending on the degree of decrease in the pressure contact force and the size of the gap, it becomes difficult to maintain the sealability between the boot and the shaft over a long period of time, resulting in early grease leakage. May occur or dust or water may enter from the outside.

上記した特許文献１のブーツには、予め、小径筒部のシール部に加熱荷重処理を施して、初期の「ヘタリ」を生じさせている。なお、加熱荷重処理では、加熱されたプレス治具によって小径筒部を縮径させている。
しかしながら、かかる処理では、ブーツの製造装置の他にプレス治具を別途用意しなければならず、また、ブーツの製造プロセスの他に加熱荷重処理プロセスが別途必要となるため、これに要する手間や時間を要し、その分だけブーツの製造コストが上昇してしまう。
また、特許文献１に記載のブーツでは、雰囲気温度が高温（エンジン駆動時）から低温（エンジン停止時）に低下した場合のシール性の低下については、何ら検討はされていない。
一方、シャフトに圧接する突状シールの先端側に微小突起を形成し、高温雰囲気下においては、かかる微小突起を潰すことにより、「ヘタリ」によるシール性の低下を防止するものも提案されているが、この提案においても、雰囲気温度が高温（エンジン駆動時）から低温（エンジン停止時）に低下した場合のシール性の低下については、何ら検討はされていない。 In the boot of Patent Document 1 described above, a heat load process is performed in advance on the seal portion of the small-diameter cylindrical portion to cause initial “sagging”. In the heating load process, the small-diameter cylindrical portion is reduced in diameter by a heated pressing jig.
However, in this process, a press jig must be separately prepared in addition to the boot manufacturing apparatus, and a heating load processing process is separately required in addition to the boot manufacturing process. Time is required, and the manufacturing cost of the boot increases accordingly.
Further, in the boot described in Patent Document 1, no study has been made on a decrease in sealing performance when the ambient temperature is decreased from a high temperature (when the engine is driven) to a low temperature (when the engine is stopped).
On the other hand, there has also been proposed a method in which a minute protrusion is formed on the tip side of a projecting seal that is in pressure contact with the shaft, and, in a high temperature atmosphere, the minute protrusion is crushed to prevent deterioration of the sealing property due to “sagging”. However, even in this proposal, no consideration has been given to a decrease in sealing performance when the ambient temperature decreases from a high temperature (when the engine is driven) to a low temperature (when the engine is stopped).

そこで、本発明の目的は、高温と低温とが繰り返される雰囲気中であっても、等速ジョイント用樹脂製ブーツと等速ジョイントのシャフト又はアウターケースとの間のシール性を簡単に、かつ、低コストで向上させると共に、そのシール性を長期に亘って維持することが可能なシール構造を提供することにある。 Therefore, the object of the present invention is to provide a simple seal between the constant velocity joint resin boot and the constant velocity joint shaft or outer case, even in an atmosphere where high and low temperatures are repeated, and An object of the present invention is to provide a sealing structure that can be improved at low cost and can maintain its sealing performance over a long period of time.

このような目的を達成するために、本発明は、等速ジョイント用樹脂製ブーツの小径側端部が等速ジョイントのシャフトに締結部材によって締結された状態で、前記小径側端部と前記シャフトとの間に構成されるシール構造であって、前記小径側端部には、前記締結部材によって締め付ける領域の内周面に沿って周方向に連続し、かつ、前記内周面から中心方向に突出した突状シールが設けられており、前記シャフトの外周面には、前記締結部材によって前記小径側端部が前記シャフトに締結された状態において、前記突状シールが弾性変形により湾曲して収容される収容空間が設けられており、前記突状シールは、前記シャフトに圧接した状態を維持しつつ、前記締結部材の締結力によって圧潰することなく、使用環境の雰囲気温度の変化に起因して前記収容空間内で熱膨張及び熱収縮による弾性変形が許容されており、前記収容空間の軸方向の両側には、前記締結部材によって前記小径側端部の内周面を前記シャフトの外周面に締め付けるための領域が設けられている。
また、本発明は、等速ジョイント用樹脂製ブーツの小径側端部が等速ジョイントのシャフトに締結部材によって締結された状態で、前記小径側端部と前記シャフトとの間に構成されるシール構造であって、前記小径側端部には、前記締結部材によって締め付ける領域の内周面に沿って周方向に連続し、かつ、前記内周面から中心方向に突出した突状シールが設けられており、前記小径側端部の内周面には、前記締結部材によって前記小径側端部が前記シャフトに締結された状態において、前記突状シールが弾性変形により湾曲して収容される収容空間が設けられており、前記突状シールは、前記シャフトに圧接した状態を維持しつつ、前記締結部材の締結力によって圧潰することなく、使用環境の雰囲気温度の変化に起因して前記収容空間内で熱膨張及び熱収縮による弾性変形が許容されており、前記収容空間の軸方向の両側には、前記締結部材によって前記小径側端部の内周面を前記シャフトの外周面に締め付けるための領域が設けられている。
また、本発明は、等速ジョイント用樹脂製ブーツの大径側端部が等速ジョイントのアウターケースに締結部材によって締結された状態で、前記大径側端部と前記アウターケースとの間に構成されるシール構造であって、前記大径側端部には、前記締結部材によって締め付ける領域の内周面に沿って周方向に連続し、かつ、前記内周面から中心方向に突出した突状シールが設けられており、前記アウターケースの外周面には、前記締結部材によって前記大径側端部が前記アウターケースに締結された状態において、前記突状シールが弾性変形により湾曲して収容される収容空間が設けられており、前記突状シールは、前記アウターケースに圧接した状態を維持しつつ、前記締結部材の締結力によって圧潰することなく、使用環境の雰囲気温度の変化に起因して前記収容空間内で熱膨張及び熱収縮による弾性変形が許容されており、前記収容空間の軸方向の両側には、前記締結部材によって前記大径側端部の内周面を前記アウターケースの外周面に締め付けるための領域が設けられている。
また、本発明は、等速ジョイント用樹脂製ブーツの大径側端部が等速ジョイントのアウターケースに締結部材によって締結された状態で、前記大径側端部と前記アウターケースとの間に構成されるシール構造であって、前記大径側端部には、前記締結部材によって締め付ける領域の内周面に沿って周方向に連続し、かつ、前記内周面から中心方向に突出した突状シールが設けられており、前記大径側端部の内周面には、前記締結部材によって前記大径側端部が前記アウターケースに締結された状態において、前記突状シールが弾性変形により湾曲して収容される収容空間が設けられており、前記突状シールは、前記アウターケースに圧接した状態を維持しつつ、前記締結部材の締結力によって圧潰することなく、使用環境の雰囲気温度の変化に起因して前記収容空間内で熱膨張及び熱収縮による弾性変形が許容されており、前記収容空間の軸方向の両側には、前記締結部材によって前記大径側端部の内周面を前記アウターケースの外周面に締め付けるための領域が設けられている。
本発明において、前記収容空間は、前記シャフトの外周面に沿って周方向に連続して形成され、かつ、前記突状シールに対向する領域を含んだ所定範囲を所定量窪ませて形成されている。
本発明において、前記収容空間は、前記アウターケースの外周面に沿って周方向に連続して形成され、かつ、前記突状シールに対向する領域を含んだ所定範囲を所定量窪ませて形成されている。
本発明において、前記収容空間は、前記小径側端部の内周面に沿って周方向に連続して形成され、かつ、前記突状シールを含んだ所定範囲を所定量窪ませて形成されている。
本発明において、前記収容空間は、前記大径側端部の内周面に沿って周方向に連続して形成され、かつ、前記突状シールを含んだ所定範囲を所定量窪ませて形成されている。
本発明において、前記小径側端部を前記シャフトに装着する際に、前記突状シールを前記収容空間に収容した状態に位置決めするための位置決め手段を備えている。
In order to achieve such an object, the present invention provides the small diameter side end portion and the shaft in a state where the small diameter side end portion of the resin boot for constant velocity joint is fastened to the shaft of the constant velocity joint by a fastening member. The small-diameter side end is continuous in the circumferential direction along the inner peripheral surface of the region to be tightened by the fastening member, and from the inner peripheral surface to the central direction. A protruding projecting seal is provided, and the projecting seal is accommodated on the outer peripheral surface of the shaft in a state where the end portion on the small diameter side is fastened to the shaft by the fastening member due to elastic deformation. is provided with a receiving space that is, the projecting seal, while maintaining a state of being pressed against the shaft without collapsing by the fastening force of the fastening member, a change in ambient temperature of the operating environment Due to which the elastic deformation is permitted by the thermal expansion and contraction in the accommodating space, the both sides in the axial direction of the accommodating space, the inner peripheral surface of the smaller diameter end by the fastening member of said shaft A region for fastening to the outer peripheral surface is provided.
The present invention, in a state where the smaller diameter end of the constant velocity joint for plastic boot is fastened by the fastening member to Shah shift of the constant velocity joint, constructed between the shaft and the smaller diameter end In the seal structure, the small diameter side end portion is provided with a projecting seal that is continuous in the circumferential direction along the inner peripheral surface of the region to be tightened by the fastening member and protrudes in the center direction from the inner peripheral surface. In the state where the small diameter side end is fastened to the shaft by the fastening member, the protruding seal is accommodated in the inner peripheral surface of the small diameter side end by being bent by elastic deformation. A space is provided, and the projecting seal is maintained in a state of being pressed against the shaft, and is not crushed by a fastening force of the fastening member, and is caused by a change in an ambient temperature of a use environment. Inside Are permitted elastic deformation due to thermal expansion and thermal contraction, the both sides in the axial direction of the accommodating space, the area for clamping the inner peripheral surface of the smaller diameter end to the outer peripheral surface of the sheet Yafuto by said fastening member Is provided.
The present invention, in a state where the large diameter side end portion of the resin boot for a constant velocity joint is fastened by the fastening member to the Au terpolymers case of the constant velocity joint, between said larger diameter end outer case a seal structure configured, wherein the larger diameter end, the continuously in the circumferential direction along the inner circumferential surface of the region put tighten the fastening member, and toward the center from the inner peripheral surface projecting and projecting seal is provided with, wherein the outer peripheral surface of the outer case, in a state in which the by the fastening member larger diameter end is fastened to the outer casing, wherein the projecting seal elastic deformation is provided with a receiving space which is accommodated in a curved manner, the projecting seal, while maintaining a state of being pressed against the a Utakesu, without crushing by the fastening force of the fastening member, the atmosphere of the environment of use Temperature Of which elastic deformation is permitted due to thermal expansion and thermal contraction due to the accommodating space, the both sides in the axial direction of the accommodating space, the inner peripheral surface of the front SL larger diameter end by the fastening member area for clamping on the outer peripheral surface of the outer case is provided.
The present invention, in a state where the large diameter side end portion of the resin boot for a constant velocity joint is fastened by the fastening member to the Au terpolymers case of the constant velocity joint, between said larger diameter end outer case a seal structure configured, wherein the larger diameter end, the continuously in the circumferential direction along the inner circumferential surface of the region put tighten the fastening member, and toward the center from the inner peripheral surface projecting projecting seal is provided with, wherein the inner peripheral surface of the large diameter side end portion, in a state where the front SL larger diameter end is fastened to the outer casing by the fastening member, the protruding seal There is provided with a receiving space which is accommodated in a curved by elastic deformation, the projecting seal, while maintaining a state of being pressed against the outer Kesu, without crushing by the fastening force of the fastening member, using Changes in ambient atmospheric temperature Due to which the elastic deformation is permitted by the thermal expansion and contraction in the accommodating space, the both sides in the axial direction of the accommodation space, the outer and inner peripheral surfaces of the larger diameter end by the fastening member area for clamping on the outer peripheral surface of the case is that provided.
In the present invention, the storage space is formed continuously in the circumferential direction along the outer peripheral surface of the shaft, and is formed by recessing a predetermined range including a region facing the protruding seal by a predetermined amount. Yes.
In the present invention, the storage space is formed continuously in the circumferential direction along the outer peripheral surface of the outer case, and is formed by depressing a predetermined range including a region facing the protruding seal by a predetermined amount. ing.
In the present invention, the accommodation space is formed continuously in the circumferential direction along the inner peripheral surface of the end portion on the small diameter side, and is formed by depressing a predetermined range including the protruding seal by a predetermined amount. Yes.
In the present invention, the storage space is formed continuously in the circumferential direction along the inner peripheral surface of the large-diameter end, and is formed by recessing a predetermined range including the protruding seal by a predetermined amount. ing.
In the present invention, when the small diameter side end is mounted on the shaft, positioning means is provided for positioning the protruding seal in a state of being accommodated in the accommodating space.

本発明によれば、高温と低温とが繰り返される雰囲気中であっても、等速ジョイント用樹脂製ブーツと等速ジョイントのシャフト又はアウターケースとの間のシール性を簡単に、かつ、低コストで向上させると共に、そのシール性を長期に亘って維持することが可能となる。 According to the present invention, the sealing performance between the constant velocity joint resin boot and the constant velocity joint shaft or outer case can be easily and low-cost even in an atmosphere where high and low temperatures are repeated. In addition, the sealing performance can be maintained for a long time.

以下、本発明の一実施の形態に係るシール構造について、図１(ａ)〜(ｅ)及び図２を参照して説明する。本実施の形態において、等速ジョイント２に装着される樹脂製のブーツ４は、当該ブーツ４の両端側を締結部材６,８によって締め付けて等速ジョイント２のシャフト２ａ及びアウターケース（ギヤハウジングともいう）２ｂに締結されている。なお、ブーツ４の成形材料としての樹脂は、例えばポリエステル系の熱可塑性エラストマ等の熱可塑性樹脂を適用することができるが、これ以外の成形材料でも良い。 A seal structure according to an embodiment of the present invention will be described below with reference to FIGS. 1 (a) to 1 (e) and FIG. In the present embodiment, the resin boot 4 attached to the constant velocity joint 2 is formed by tightening both ends of the boot 4 with the fastening members 6 and 8 and the shaft 2a of the constant velocity joint 2 and the outer case (both the gear housing). It is fastened to 2b. For example, a thermoplastic resin such as a polyester-based thermoplastic elastomer can be applied as the resin as the molding material of the boot 4, but other molding materials may be used.

図１(ａ)に示すように、ブーツ４には、その一端側に中空円筒形の小径側端部Ｐ１が設けられていると共に、当該ブーツ４の他端側には、小径側端部Ｐ１よりも大径を成した中空円筒形の大径側端部Ｐ３が設けられている。この場合、小径側端部Ｐ１は、小径側締結部材６（以下、小径側締結用バンドという）によって等速ジョイント２のシャフト２ａに締結され、一方、大径側端部Ｐ３は、大径側締結部材８（以下、大径側締結用バンドという）によって等速ジョイント２のアウターケース２ｂに締結されるようになっている。 As shown in FIG. 1A, the boot 4 is provided with a hollow cylindrical small-diameter side end portion P1 on one end side thereof, and the boot 4 has a small-diameter side end portion P1 on the other end side thereof. A hollow-cylindrical large-diameter side end portion P3 having a larger diameter is provided. In this case, the small diameter side end P1 is fastened to the shaft 2a of the constant velocity joint 2 by a small diameter side fastening member 6 (hereinafter referred to as a small diameter side fastening band), while the large diameter side end P3 is The fastening member 8 (hereinafter referred to as a large-diameter side fastening band) is fastened to the outer case 2b of the constant velocity joint 2.

また、小径側端部Ｐ１と大径側端部Ｐ３との間には、等速ジョイント２のシャフト２ａとアウターケース２ｂとの相対的な角度変化に追従して弾性変形する中空円錐形の蛇腹部Ｐ２が設けられている。蛇腹部Ｐ２は、小径側端部Ｐ１に連続した環状の肩部Ｋから大径側端部Ｐ３に向って末広がり形状を成し、複数の環状山部Ｍと環状谷部Ｖとを交互に組み合わせて構成されている。これにより、蛇腹部Ｐ２は、弾性的に伸縮変形自在な状態に維持される。 Further, between the small-diameter side end P1 and the large-diameter side end P3, a hollow conical bellows that elastically deforms following a relative angular change between the shaft 2a of the constant velocity joint 2 and the outer case 2b. Part P2 is provided. The bellows portion P2 has a divergent shape extending from the annular shoulder portion K continuous to the small diameter side end portion P1 toward the large diameter side end portion P3, and a plurality of annular mountain portions M and annular valley portions V are alternately combined. Configured. Thereby, the bellows part P2 is maintained in a state in which it can be elastically deformed elastically.

また、小径側端部Ｐ１及び大径側端部Ｐ３には、それぞれ、小径側締結用バンド６及び大径側締結用バンド８を装着するためのバンド装着部６ｐ,８ｐが設けられており、これらバンド装着部６ｐ,８ｐに小径側締結用バンド６及び大径側締結用バンド８をそれぞれ装着して締め付けることで、小径側端部Ｐ１を等速ジョイント２のシャフト２ａに締結させることができると共に、大径側端部Ｐ３を等速ジョイント２のアウターケース２ｂに締結させることができる。これにより、ブーツ４を等速ジョイント２に装着させることができる。 The small diameter side end portion P1 and the large diameter side end portion P3 are provided with band mounting portions 6p and 8p for mounting the small diameter side fastening band 6 and the large diameter side fastening band 8, respectively. By attaching and tightening the small-diameter side fastening band 6 and the large-diameter side fastening band 8 respectively to the band attaching portions 6p and 8p, the small-diameter side end portion P1 can be fastened to the shaft 2a of the constant velocity joint 2. At the same time, the large-diameter end P3 can be fastened to the outer case 2b of the constant velocity joint 2. Thereby, the boot 4 can be attached to the constant velocity joint 2.

本実施の形態のシール構造は、小径側締結用バンド６によって互いに締結されるブーツ４の小径側端部Ｐ１（バンド装着部６ｐ）と等速ジョイント２のシャフト２ａとの間、及び、大径側締結用バンド８によって互いに締結されるブーツ４の大径側端部Ｐ３（バンド装着部８ｐ）と等速ジョイント２のアウターケース２ｂとの間に構成することができる。この場合、双方のシール構造は、互いに同一の構成とすることができるため、以下では一例として、ブーツ４の小径側端部Ｐ１（バンド装着部６ｐ）と等速ジョイント２のシャフト２ａとの間に構成されるシール構造について説明する。 The seal structure of the present embodiment has a small diameter side end portion P1 (band mounting portion 6p) of the boot 4 fastened to each other by the small diameter side fastening band 6 and the shaft 2a of the constant velocity joint 2, and a large diameter. A large-diameter side end portion P3 (band mounting portion 8p) of the boot 4 fastened to each other by the side fastening band 8 and the outer case 2b of the constant velocity joint 2 can be formed. In this case, since both the seal structures can have the same configuration, as an example, between the small diameter side end portion P1 (band mounting portion 6p) of the boot 4 and the shaft 2a of the constant velocity joint 2 below. A seal structure configured as described above will be described.

図１(ｃ)〜(ｅ)に示すように、ブーツ４には、小径側締結用バンド６によって締め付ける領域（小径側端部Ｐ１のバンド装着部６ｐ）の内周面Ｐｓに沿って周方向に連続し、かつ、内周面Ｐｓを部分的に少なくとも１箇所を中心方向に突出させて形成した突状シール１０が設けられている。一例として図面には、１つの突状シール１０が示されている。
この突状シール１０は、ブーツ４を等速ジョイント２に装着していない状態においては、内周面Ｐｓに対して略垂直な方向に突出しており、また、ブーツ４の小径側端部Ｐ１を等速ジョイント２のシャフト２ａに装着して後述する収容空間１２に収容されると、弾性変形によって容易に湾曲可能に形成されている。 As shown in FIGS. 1 (c) to 1 (e), the boot 4 has a circumferential direction along the inner peripheral surface Ps of the region (band mounting portion 6 p of the small diameter side end portion P 1) tightened by the small diameter side fastening band 6. And a projecting seal 10 formed by partially projecting the inner peripheral surface Ps partially in the central direction. As an example, one protruding seal 10 is shown in the drawing.
The protruding seal 10 protrudes in a direction substantially perpendicular to the inner peripheral surface Ps when the boot 4 is not attached to the constant velocity joint 2, and the small diameter side end portion P1 of the boot 4 is formed. When mounted on the shaft 2a of the constant velocity joint 2 and accommodated in the accommodation space 12 described later, the elastic joint is formed so as to be easily bent by elastic deformation.

一方、等速ジョイント２のシャフト２ａの外周面２ｓには、小径側締結用バンド６によってブーツ４の小径側端部Ｐ１（バンド装着部６ｐ）とシャフト２ａとが互いに締結された状態において、突状シール１０が弾性変形により湾曲して収容される収容空間１２が設けられている。 On the other hand, on the outer peripheral surface 2s of the shaft 2a of the constant velocity joint 2, the small diameter side end portion P1 (band mounting portion 6p) of the boot 4 and the shaft 2a are fastened together by the small diameter side fastening band 6. An accommodation space 12 in which the cylindrical seal 10 is accommodated by being bent by elastic deformation is provided.

ここで、突状シール１０は、小径側締結用バンド６によって小径側端部Ｐ１（バンド装着部６ｐ）とシャフト２ａとが互いに締結された状態（以下、バンド締結状態という）において、突出端１０ｔ側から内周面Ｐｓ側にかけての側面（１０ａ又は１０ｂ）がシャフト２ａの外周面２ｓ（本実施の形態では、後述する収容空間１２の収容空間構成面１２ｓ）に対して弾性変形により湾曲するとともに、弾性復元力によりシャフト２ａの外周面２ｓ（本実施の形態では、後述する収容空間１２の収容空間構成面１２ｓ）に圧接して所定の面圧を維持するように形成されている。
また、突状シール１０において、使用環境の雰囲気温度の変化に起因する熱膨張及び熱収縮による変形は、突状シール１０の湾曲状態の変化や突状シール１０の突出端１０ｔ側の位置ずれ等によって許容できるように構成されている。
このため、本実施の形態においては、従来のように、突状シール１０の熱膨張による変形がバンド締結力によって規制されておらず、シャフト２ａの収容空間１２内において許容されているため、突状シール１０の「ヘタリ」の発生を極力抑えることができる構成となっている。 Here, the protruding seal 10 has a protruding end 10t in a state in which the small diameter side end portion P1 (band mounting portion 6p) and the shaft 2a are fastened to each other by the small diameter side fastening band 6 (hereinafter referred to as a band fastened state). The side surface (10a or 10b) from the side to the inner peripheral surface Ps side is curved by elastic deformation with respect to the outer peripheral surface 2s of the shaft 2a (in the present embodiment, a storage space constituting surface 12s of the storage space 12 described later). The outer circumferential surface 2s of the shaft 2a (in the present embodiment, a housing space constituting surface 12s of the housing space 12 described later) is pressed against the outer surface 2s of the shaft 2a to maintain a predetermined surface pressure.
Further, in the projecting seal 10, deformation due to thermal expansion and contraction caused by a change in the ambient temperature of the usage environment is caused by a change in the curved state of the projecting seal 10, a positional deviation on the projecting end 10 t side of the projecting seal 10, etc. Is configured to be acceptable.
For this reason, in the present embodiment, unlike the conventional case, deformation due to thermal expansion of the projecting seal 10 is not restricted by the band fastening force and is allowed in the housing space 12 of the shaft 2a. It is the structure which can suppress generation | occurrence | production of the "stickiness" of the shape seal 10 as much as possible.

さらに説明すると、突状シール１０は、ブーツ４の大径側端部Ｐ３側に対峙した第１の側面１０ａと、これとは反対側に対峙した第２の側面１０ｂとを有している。第１の側面１０ａは、突出端１０ｔから小径側端部Ｐ１（バンド装着部６ｐ）の内周面Ｐｓにかけて滑らかに連続しおり、一方、第２の側面１０ｂは、突出端１０ｔから小径側端部Ｐ１（バンド装着部６ｐ）の内周面Ｐｓにかけて滑らかに連続している。 More specifically, the projecting seal 10 has a first side face 10a facing the large-diameter side end portion P3 of the boot 4 and a second side face 10b facing the opposite side. The first side surface 10a is smoothly continuous from the protruding end 10t to the inner peripheral surface Ps of the small diameter side end portion P1 (band mounting portion 6p), while the second side surface 10b is connected to the small diameter side end portion from the protruding end 10t. It is smoothly continuous over the inner peripheral surface Ps of P1 (band mounting portion 6p).

この場合、第１の側面１０ａと内周面Ｐｓとの連続部位Ｒａ及び第２の側面１０ｂと内周面Ｐｓとの連続部位Ｒｂは、それぞれ、所定の曲率半径Ｒを成した丸みを帯びた形状に設定することが好ましい。これにより、突状シール１０が弾性変形した際に、それぞれの連続部位Ｒａ,Ｒｂにおける応力集中を回避することができる。なお、各連続部位Ｒａ,Ｒｂの曲率半径Ｒは、例えば突状シール１０の大きさや形状などに応じて任意に設定されるため、ここでは特に数値限定はしない。 In this case, the continuous portion Ra between the first side surface 10a and the inner peripheral surface Ps and the continuous portion Rb between the second side surface 10b and the inner peripheral surface Ps are rounded with a predetermined radius of curvature R, respectively. It is preferable to set the shape. Thereby, when the projecting seal 10 is elastically deformed, it is possible to avoid stress concentration in each of the continuous portions Ra and Rb. In addition, since the curvature radius R of each continuous site | part Ra and Rb is arbitrarily set, for example according to the magnitude | size, shape, etc. of the protruding seal 10, there is no numerical limitation in particular here.

また、突状シール１０の形状は、例えばそれぞれの連続部位Ｒａ,Ｒｂから突出端１０ｔに向けて第１の側面１０ａと第２の側面１０ｂとの間隔が徐々に（連続的に）小さくなった先細り形状、或いは、例えばそれぞれの連続部位Ｒａ,Ｒｂから突出端１０ｔに向けて第１の側面１０ａと第２の側面１０ｂとの間隔が一定となったストレート形状など、任意の形状とすることができる。図１には一例として、先細り形状の突状シール１０が示されているが、これはあくまで例示であり、これにより発明の技術的範囲が限定されるものではない。なお、どのような形状とした場合でも、突出端１０ｔは、半円弧状に丸みを帯びた形状とすることが好ましい。 Further, the shape of the protruding seal 10 is such that the distance between the first side surface 10a and the second side surface 10b gradually (continuously) decreases from the respective continuous portions Ra and Rb toward the protruding end 10t, for example. The shape may be any shape such as a tapered shape or a straight shape in which the distance between the first side surface 10a and the second side surface 10b is constant from the respective continuous portions Ra and Rb toward the protruding end 10t. it can. FIG. 1 shows a tapered projecting seal 10 as an example, but this is merely an example, and the technical scope of the present invention is not limited thereby. In any case, it is preferable that the projecting end 10t has a semicircular arc shape that is rounded.

また、突状シール１０の厚さＷは、第１の側面１０ａと第２の側面１０ｂとの間隔によって規定されるが、上記した先細り形状やストレート形状などを含めた平均の厚さＷ（例えば、後述する突出長の中心位置の厚さＷ）を想定すると、突状シール１０は、例えば突出端１０ｔ側に負荷された力によって弾性変形自在に湾曲可能な厚さＷに設定することが好ましい。具体的には、突状シール１０の厚さＷは、バンド締結状態において、突出端１０ｔ側を構成する第１の側面１０ａ又は第２の側面１０ｂがシャフト２ａの外周面２ｓ（本実施の形態では、後述する収容空間１２の収容空間構成面１２ｓ）に当接して弾性変形により湾曲するとともに、弾性復元力により圧接して所定の面圧を維持できるような厚さＷに設定されている。なお、突状シール１０の厚さＷは、例えば突状シール１０の大きさや形状、及び後述する突出長Ｈなどに応じて任意に設定されるため、ここでは特に数値限定はしない。また、突状シール１０の厚さＷについては、高温雰囲気下において、突状シール１０が熱膨張した場合であっても、かかる熱膨張による変形を、当該突状シール１０自身の湾曲状態の変化や突出端１０ｔ側の位置ずれ等によって許容できるような厚さＷに設定されている。 Further, the thickness W of the projecting seal 10 is defined by the distance between the first side surface 10a and the second side surface 10b, but the average thickness W including the tapered shape and the straight shape described above (for example, Assuming a thickness W of the center position of the protruding length described later, the protruding seal 10 is preferably set to a thickness W that can be elastically deformed by a force applied to the protruding end 10t side, for example. . Specifically, the thickness W of the protruding seal 10 is such that, in the band fastening state, the first side surface 10a or the second side surface 10b constituting the protruding end 10t side is the outer peripheral surface 2s of the shaft 2a (this embodiment). In this case, the thickness W is set to a thickness W that abuts against a housing space constituting surface 12s) of the housing space 12 to be described later and is curved by elastic deformation and can be pressed by an elastic restoring force to maintain a predetermined surface pressure. Note that the thickness W of the projecting seal 10 is arbitrarily set according to the size and shape of the projecting seal 10 and the projection length H, which will be described later. Further, regarding the thickness W of the projecting seal 10, even when the projecting seal 10 is thermally expanded in a high temperature atmosphere, the deformation due to the thermal expansion is caused by the change in the curved state of the projecting seal 10 itself. Further, the thickness W is set such that it can be tolerated by the positional deviation on the protruding end 10t side.

また、突状シール１０の突出長Ｈは、ブーツ４の小径側端部Ｐ１におけるバンド装着部６ｐの内周面Ｐｓから突出端１０ｔまでの長さ（或いは、内周面Ｐｓに垂直な方向で捉えた場合には、高さ）として規定されるが、突状シール１０は、突出端１０ｔ側を構成する側面（１０ａ又は１０ｂ）がシャフト２ａの外周面２ｓ（本実施の形態では、後述する収容空間１２の収容空間構成面１２ｓ）に当接して弾性変形により湾曲するとともに、弾性復元力により圧接して所定の面圧を維持できるような突出長Ｈに設定されている。
具体的には、突状シール１０の突出長Ｈは、バンド締結状態において、後述する収容空間１２に当該突状シール１０が収容可能な突出長Ｈであって、かつ、その状態で、突出端１０ｔ側を構成する側面（１０ａ又は１０ｂ）がシャフト２ａの外周面２ｓ（後述する収容空間構成面１２ｓ）に対して弾性変形自在に湾曲して圧接するような突出長Ｈに設定すれば良い。なお、突状シール１０の突出長Ｈは、例えば突状シール１０の大きさや形状、上記した厚さＷ、及び後述する収容空間１２の広さや収容空間構成面１２ｓの形状などに応じて任意に設定されるため、ここでは特に数値限定はしない。 The protruding length H of the protruding seal 10 is the length from the inner peripheral surface Ps of the band mounting portion 6p to the protruding end 10t at the small diameter side end portion P1 of the boot 4 (or in a direction perpendicular to the inner peripheral surface Ps). In this case, the protruding seal 10 has a side surface (10a or 10b) constituting the protruding end 10t side of the outer peripheral surface 2s of the shaft 2a (described later in this embodiment). The protrusion length H is set so as to be in contact with the storage space constituting surface 12s) of the storage space 12 and to bend by elastic deformation, and to be kept in contact with the elastic restoring force to maintain a predetermined surface pressure.
Specifically, the projecting length H of the projecting seal 10 is the projecting length H that can accommodate the projecting seal 10 in the accommodating space 12 described later in the band fastening state, and in this state, the projecting end The protruding length H may be set such that the side surface (10a or 10b) constituting the 10t side is elastically deformed and pressed against the outer peripheral surface 2s (accommodating space forming surface 12s described later) of the shaft 2a. The protruding length H of the projecting seal 10 is arbitrarily selected according to, for example, the size and shape of the projecting seal 10, the above-described thickness W, the size of the accommodating space 12 described later, and the shape of the accommodating space constituting surface 12s. Since it is set, the numerical value is not particularly limited here.

また、突状シール１０の突出方向は、図１には一例として、内周面Ｐｓに垂直な方向に突出した突状シール１０が示されているが、これに限定されることはなく、例えばブーツ４の大径側端部Ｐ３側に向けて傾斜させても良いし、或いは、これとは反対側に向けて傾斜させても良い。図４(ａ)には一例として、ブーツ４の大径側端部Ｐ３側に向けて傾斜させた突状シール１０が示されている。ここで、内周面Ｐｓに垂直な方向に延在する基準面Ｘを想定し、また、突状シール１０の傾斜方向として、突出端１０ｔと各連続部位Ｒａ,Ｒｂの中央部分とを通る傾斜軸Ｙを想定すると、突状シール１０の傾斜角度θは、基準面Ｘに対する傾斜軸Ｙの成す角として規定することができる。この場合、傾斜角度θは、例えば後述するセルフシール効果を得るため、或いは、シャフト２ａに対するブーツ４の小径側端部Ｐ１の装着のし易さなどに応じて任意に設定されるため、ここでは特に数値限定はしない。 In addition, the protruding direction of the protruding seal 10 is shown in FIG. 1 as an example, but the protruding seal 10 protruding in a direction perpendicular to the inner peripheral surface Ps is shown, but the present invention is not limited to this. The boot 4 may be inclined toward the large-diameter side end portion P3, or may be inclined toward the opposite side. FIG. 4A shows, as an example, a protruding seal 10 that is inclined toward the large-diameter side end portion P3 of the boot 4. Here, a reference plane X extending in a direction perpendicular to the inner peripheral surface Ps is assumed, and as an inclination direction of the projecting seal 10, an inclination passing through the projecting end 10t and the central portion of each continuous portion Ra, Rb. Assuming the axis Y, the inclination angle θ of the protruding seal 10 can be defined as the angle formed by the inclination axis Y with respect to the reference plane X. In this case, the inclination angle θ is arbitrarily set according to, for example, the self-sealing effect described later or the ease of mounting the small diameter side end portion P1 of the boot 4 to the shaft 2a. There is no particular numerical limitation.

一方、収容空間１２は、シャフト２ａの外周面２ｓに沿って周方向に連続して形成され、かつ、上記した突状シール１０に対向する領域を含んだ所定範囲を所定量窪ませて形成されている。収容空間１２は、シャフト２ａの外周面２ｓよりも窪ませて形成した収容空間構成面１２ｓを有している。この場合、バンド締結状態において、収容空間構成面１２ｓと小径側端部Ｐ１（バンド装着部６ｐ）の内周面Ｐｓとの間に、突状シール１０を収容し、かつ、突状シール１０の突出端１０ｔ側が弾性変形によって湾曲可能な許容可能な収容空間１２が構成されることになる。 On the other hand, the accommodating space 12 is formed continuously in the circumferential direction along the outer peripheral surface 2s of the shaft 2a, and is formed by depressing a predetermined range including a region facing the protruding seal 10 by a predetermined amount. ing. The housing space 12 has a housing space constituting surface 12s formed so as to be recessed from the outer peripheral surface 2s of the shaft 2a. In this case, in the band fastening state, the projecting seal 10 is accommodated between the housing space constituting surface 12s and the inner peripheral surface Ps of the small diameter side end portion P1 (band mounting portion 6p). An allowable storage space 12 is formed in which the protruding end 10t side can be bent by elastic deformation.

ここで、収容空間１２の大きさや形状は、収容空間構成面１２ｓの窪み量や窪み形状に応じて任意に設定することができる。図１には一例として、収容空間構成面１２ｓを円弧状に窪ませた収容空間１２が示されているが、これに限定されることはなく、例えば矩形状や楕円状など任意に収容空間構成面１２ｓを窪ませることができる。要するに、バンド締結状態において、突状シール１０が収容可能な大きさや形状の収容空間１２となるように収容空間構成面１２ｓを設定すれば良い。この場合、収容空間構成面１２ｓの窪み量や窪み形状は、バンド締結状態において、突状シール１０が弾性変形自在に湾曲して収容でき、かつ、突状シール１０の突出端１０ｔ側を構成する側面（１０ａ又は１０ｂ）が弾性復元力で収容空間構成面１２ｓに圧接して所定の面圧を維持できるように設定すれば良い。 Here, the size and shape of the accommodation space 12 can be arbitrarily set according to the amount of depression and the shape of the depression of the accommodation space constituting surface 12s. As an example, FIG. 1 shows an accommodation space 12 in which an accommodation space constituting surface 12s is recessed in an arc shape, but is not limited to this, and an arbitrary accommodation space configuration such as a rectangular shape or an oval shape is possible. The surface 12s can be recessed. In short, the accommodation space constituting surface 12s may be set so that the accommodation space 12 has a size and shape that can accommodate the protruding seal 10 in the band fastening state. In this case, the depression amount and the depression shape of the accommodation space constituting surface 12 s can be accommodated by the protruding seal 10 being curved and elastically deformable in the band fastening state, and constitute the protruding end 10 t side of the protruding seal 10. The side surface (10a or 10b) may be set so that a predetermined surface pressure can be maintained by pressing against the housing space constituting surface 12s with an elastic restoring force.

なお、収容空間構成面１２ｓの窪み量は、バンド締結状態で突状シール１０の突出端１０ｔ側が圧接する当該収容空間構成面１２ｓの底面(参照符号は省略する)と、シャフト２ａの外周面２ｓと間における窪み量Ｇ（図１(ｃ)参照）として規定されるが、当該窪み量Ｇは、例えば上記した突状シール１０の突出長Ｈ（内周面Ｐｓから突出端１０ｔまでの長さ）に応じて任意に設定されるため、ここでは特に数値限定はしない。また、収容空間構成面１２ｓの形状については、少なくとも上記窪み量Ｇに相当する収容空間構成面１２ｓの底面の形状を、バンド締結状態で突状シール１０が弾性変形自在に湾曲して収容でき、かつ、突状シール１０の突出端１０ｔ側を構成する側面（１０ａ又は１０ｂ）が弾性復元力で収容空間構成面１２ｓに圧接して所定の面圧を維持できるように設定すれば良い。 It should be noted that the amount of depression of the housing space constituting surface 12s includes the bottom surface (reference numeral is omitted) of the housing space constituting surface 12s where the protruding end 10t side of the projecting seal 10 is in pressure contact with the outer peripheral surface 2s of the shaft 2a. Is defined as a recess amount G (see FIG. 1C), for example, the recess amount G is, for example, the protruding length H of the protruding seal 10 (the length from the inner peripheral surface Ps to the protruding end 10t). ) Is arbitrarily set in accordance with), and there is no particular numerical limitation here. Further, with respect to the shape of the accommodation space constituting surface 12s, at least the shape of the bottom surface of the accommodation space constituting surface 12s corresponding to the depression amount G can be accommodated while the protruding seal 10 is elastically deformed and accommodated in a band fastening state. In addition, the side surface (10a or 10b) constituting the protruding end 10t side of the projecting seal 10 may be set so as to be able to maintain a predetermined surface pressure by pressing against the housing space constituting surface 12s with an elastic restoring force.

また、本実施の形態のシール構造を構成する位置は、バンド締結状態において、突状シール１０及び収容空間１２の両側に、小径側締結用バンド６によって小径側端部Ｐ１（バンド装着部６ｐ）の内周面Ｐｓをシャフト２ａの外周面２ｓに締め付けるための締付領域Ｆ１,Ｆ２（図１(ｂ)参照）が確保されるように設定することが好ましい。同図において、ブーツ４の大径側端部Ｐ３側に締付領域Ｆ１、これと反対側に締付領域Ｆ２がそれぞれ確保されている。なお、各締付領域Ｆ１,Ｆ２の大きさ（範囲）は、例えばシャフト２ａの外周面２ｓ全体に対する収容空間１２の占める割合を考慮して任意に設定されるため、ここでは特に数値限定はしない。 Moreover, the position which comprises the seal structure of this Embodiment is the small diameter side edge part P1 (band mounting part 6p) by the small diameter side fastening band 6 on both sides of the protruding seal 10 and the accommodation space 12 in a band fastening state. It is preferable to set so that tightening regions F1 and F2 (see FIG. 1 (b)) for securing the inner peripheral surface Ps to the outer peripheral surface 2s of the shaft 2a are secured. In the figure, a fastening region F1 is secured on the large diameter side end portion P3 side of the boot 4, and a fastening region F2 is secured on the opposite side. The sizes (ranges) of the tightening regions F1 and F2 are arbitrarily set in consideration of, for example, the ratio of the accommodation space 12 to the entire outer peripheral surface 2s of the shaft 2a. .

また、本実施の形態のシール構造は、ブーツ４を等速ジョイント２のシャフト２ａに装着する際に、突状シール１０を収容空間１２に収容した状態で位置決めするための位置決め手段を備えている。位置決め手段として、小径側端部Ｐ１（バンド装着部６ｐ）の内周面Ｐｓには、その一部を内向き（中心方向）に突出させて形成した突出部１４が設けられていると共に、シャフト２ａの外周面２ｓには、突出部１４が係合可能に窪ませた窪み部１６が設けられている。この場合、突出部１４及び窪み部１６は、周方向に沿って連続して構成することが好ましい。 Further, the seal structure of the present embodiment is provided with positioning means for positioning the protruding seal 10 in a state in which it is accommodated in the accommodating space 12 when the boot 4 is attached to the shaft 2 a of the constant velocity joint 2. . As positioning means, the inner peripheral surface Ps of the small-diameter side end portion P1 (band mounting portion 6p) is provided with a projecting portion 14 formed by projecting a part thereof inward (center direction), and a shaft. The outer peripheral surface 2s of 2a is provided with a recess 16 in which the protrusion 14 is recessed so as to be engageable. In this case, it is preferable that the protrusion part 14 and the hollow part 16 are comprised continuously along the circumferential direction.

なお、図１(ｂ)〜(ｄ)に示された位置決め手段は、あくまで例示であり、これにより発明の技術的範囲が限定されるものではない。例えば図１の構成とは逆に、小径側端部Ｐ１（バンド装着部６ｐ）の内周面Ｐｓに窪み部(図示しない)を設けると共に、シャフト２ａの外周面２ｓに突出部(図示しない)を設けても良い。また、突出部１４及び窪み部１６の形状は、図１のような円弧状以外に例えば楕円状や矩形状など、互いに係合可能な形状であれば任意に設定することができる。更に、位置決め手段の配置は、図１の配置構成に限定されることはなく、突出部１４及び窪み部１６を形成できるような部位であれば任意に設定することができる。また、上記の位置決め手段を設けるか否かも任意である。 The positioning means shown in FIGS. 1B to 1D are merely examples, and the technical scope of the invention is not limited thereby. For example, contrary to the configuration of FIG. 1, a recess (not shown) is provided on the inner peripheral surface Ps of the small diameter side end portion P1 (band mounting portion 6p), and a protruding portion (not shown) is provided on the outer peripheral surface 2s of the shaft 2a. May be provided. Moreover, the shape of the protrusion part 14 and the hollow part 16 can be arbitrarily set if it is a shape which can be mutually engaged, such as elliptical shape and a rectangular shape other than circular arc shape like FIG. Furthermore, the arrangement of the positioning means is not limited to the arrangement shown in FIG. 1, and can be arbitrarily set as long as it can form the protrusions 14 and the depressions 16. Further, whether or not the positioning means is provided is also arbitrary.

以上、本実施の形態によれば、ブーツ４を等速ジョイント２に装着させる際、ブーツ４の小径側端部Ｐ１を等速ジョイント２のシャフト２ａに組み付けるとき、小径側端部Ｐ１（バンド装着部６ｐ）の内周面Ｐｓに形成された突出部１４と、シャフト２ａの外周面２ｓに形成された窪み部１６とを係合させることで、小径側端部Ｐ１（バンド装着部６ｐ）の内周面Ｐｓに形成された突状シール１０を、シャフト２ａの外周面２ｓに形成された収容空間１２に正確に位置決めさせることができる。また、突状シール１０の突出端１０ｔは、半円弧状に丸みを帯びた形状となっているため、小径側端部Ｐ１をシャフト２ａに組み付ける際、突出端１０ｔとシャフト２ａの外周面２ｓとの摺接による摩擦抵抗を低減させることができる。これにより、小径側端部Ｐ１をシャフト２ａにスムーズに組み付けることができる。 As described above, according to the present embodiment, when the boot 4 is attached to the constant velocity joint 2, when the small diameter side end portion P1 of the boot 4 is assembled to the shaft 2a of the constant velocity joint 2, the small diameter side end portion P1 (band attachment) By engaging the protrusion 14 formed on the inner peripheral surface Ps of the portion 6p) with the recess 16 formed on the outer peripheral surface 2s of the shaft 2a, the small-diameter end P1 (band mounting portion 6p) The protruding seal 10 formed on the inner peripheral surface Ps can be accurately positioned in the accommodation space 12 formed on the outer peripheral surface 2s of the shaft 2a. Further, since the protruding end 10t of the protruding seal 10 has a semicircular arc shape, when the small diameter side end portion P1 is assembled to the shaft 2a, the protruding end 10t and the outer peripheral surface 2s of the shaft 2a The frictional resistance due to the sliding contact can be reduced. Thereby, the small diameter side edge part P1 can be assembled | attached smoothly to the shaft 2a.

この状態において、突状シール１０は、弾性変形により湾曲して収容空間１２に収容される。そして、かかる状態で、小径側締結用バンド６によって小径側端部Ｐ１（バンド装着部６ｐ）とシャフト２ａとを互いに締結すると、このときの小径側締結用バンド６の締結力は、突状シール１０及び収容空間１２の両側に確保された各締付領域Ｆ１,Ｆ２に略均等に作用する。これにより、小径側端部Ｐ１（バンド装着部６ｐ）の内周面Ｐｓをシャフト２ａの外周面２ｓに対して堅牢に、かつ、強固に固定することができる。
一方、突状シール１０は、小径側締結用バンド６の締結力によって圧潰することなく、突状シール１０の突出端１０ｔ側を構成する側面（１０ａ又は１０ｂ）がシャフト２ａの外周面２ｓ（本実施の形態では、収容空間１２の収容空間構成面１２ｓ）に対して弾性変形自在に湾曲して圧接し、所定の面圧を維持している。 In this state, the projecting seal 10 is bent by elastic deformation and stored in the storage space 12. In this state, when the small diameter side end portion P1 (band mounting portion 6p) and the shaft 2a are fastened to each other by the small diameter side fastening band 6, the fastening force of the small diameter side fastening band 6 at this time is a projecting seal. 10 and the tightening regions F1 and F2 secured on both sides of the accommodating space 12 act substantially equally. Thereby, the inner peripheral surface Ps of the small diameter side end portion P1 (band mounting portion 6p) can be firmly and firmly fixed to the outer peripheral surface 2s of the shaft 2a.
On the other hand, the projecting seal 10 is not crushed by the fastening force of the small-diameter side fastening band 6, and the side surface (10a or 10b) constituting the projecting end 10t side of the projecting seal 10 is the outer peripheral surface 2s of the shaft 2a. In the embodiment, the storage space constituting surface 12s) of the storage space 12 is curved to be elastically deformed and pressed to maintain a predetermined surface pressure.

このとき、突状シール１０の突出端１０ｔ側は、例えば図２に示すように、収容空間構成面１２ｓに対して、その第１の側面１０ａが湾曲して圧接する場合（図中、点線で示す）と、その第２の側面１０ｂが湾曲して圧接する場合（図中、実線で示す）がある。いずれの場合でも、湾曲した状態における突状シール１０の弾性復元力により、その突出端１０ｔ側を構成する側面（１０ａ又は１０ｂ）が収容空間１２の収容空間構成面１２ｓに最適な面圧で圧接する。これにより、シール効果が発揮されてグリース洩れを確実に防止することができる。 At this time, the protruding end 10t side of the projecting seal 10 is, for example, as shown in FIG. 2, when the first side surface 10a is curved and pressed against the housing space constituting surface 12s (indicated by a dotted line in the figure). And the second side surface 10b is curved and press-contacted (shown by a solid line in the figure). In any case, due to the elastic restoring force of the protruding seal 10 in the curved state, the side surface (10a or 10b) constituting the protruding end 10t side is pressed against the accommodation space constituting surface 12s of the accommodation space 12 with an optimum surface pressure. To do. Thereby, a sealing effect is exhibited and grease leakage can be reliably prevented.

ここで、突出端１０ｔ側を構成する第２の側面１０ｂが収容空間構成面１２ｓに湾曲して圧接する場合には、例えば小径側端部Ｐ１（バンド装着部６ｐ）の内周面Ｐｓとシャフト２ａの外周面２ｓとの間を介して収容空間１２に入り込んだグリースは、図２中矢印Ｔで示すように、突状シール１０の第１の側面１０ａに沿って突出端１０ｔ側に集中する。このとき、グリースの内圧が突出端１０ｔ側に加われば、収容空間構成面１２ｓに対する第２の側面１０ｂの面圧が大きくなり、所謂セルフシール効果を発揮させることもできる。なお、かかる効果を優先的に発揮させる仕様では、突状シール１０の突出方向を例えば図４(ａ)に示すような傾斜角度θに設定すれば良い。このようなセルフシール構造によれば、高温雰囲気下で使用するブーツ４のコンパクト化、シャフト２ａの高角度変化、並びに、等速ジョイント２の長ストローク化によるグリースの内圧アップにも対応できる。 Here, when the second side surface 10b constituting the protruding end 10t side is curved and pressed against the accommodating space constituting surface 12s, for example, the inner peripheral surface Ps of the small diameter side end portion P1 (band mounting portion 6p) and the shaft The grease that has entered the housing space 12 through the space between the outer peripheral surface 2s of 2a is concentrated on the projecting end 10t side along the first side surface 10a of the projecting seal 10 as indicated by the arrow T in FIG. . At this time, if the internal pressure of the grease is applied to the protruding end 10t side, the surface pressure of the second side surface 10b with respect to the housing space constituting surface 12s is increased, and the so-called self-sealing effect can be exhibited. In the specification that preferentially exhibits such an effect, the protruding direction of the protruding seal 10 may be set to an inclination angle θ as shown in FIG. 4A, for example. According to such a self-sealing structure, the boot 4 used in a high-temperature atmosphere can be made compact, the shaft 2a can be changed at a high angle, and the internal pressure of the grease can be increased due to the longer stroke of the constant velocity joint 2.

また、上記したバンド締結状態では、収容空間１２において、突状シール１０の突出端１０ｔ側を構成する側面（１０ａ又は１０ｂ）がシャフト２ａの収容空間構成面１２ｓに対して弾性変形自在に湾曲した状態で圧接している。このため、高温と低温とが繰り返される雰囲気中での使用に際し、高温の雰囲気下で突状シール１０が熱膨張した場合でも、その熱膨張は収容空間１２で許容され、従来のようにバンド締結力によって突状シール１０の熱膨張が規制されることはない。
この場合、図５中に実線で示すように熱膨張した突状シール１０は、突出端１０ｔ側が収容空間構成面１２ｓに沿ってずれることで、更に湾曲することができる。これにより、突出端１０ｔ側を構成する側面（１０ａ又は１０ｂ）を含めて突状シール１０には、従来のような圧縮永久歪による「ヘタリ」の発生を極力抑えることができる。なお、図５中の破線は、低温雰囲気下において熱収縮後の突状シール１０の収容状態を示している。また、図５には、突出端１０ｔ側の一方の側面１０ｂが収容空間構成面１２ｓに圧接した突状シール１０の仕様を例示したが、これとは逆に、特に図示しないが、突出端１０ｔ側の他方の側面１０ａが収容空間構成面１２ｓに圧接した突状シール１０の仕様であっても、上記同様に、従来のような圧縮永久歪による「ヘタリ」の発生を極力抑えることができる。 Further, in the band fastening state described above, in the accommodation space 12, the side surface (10a or 10b) constituting the protruding end 10t side of the projecting seal 10 is curved to be elastically deformable with respect to the accommodation space constituting surface 12s of the shaft 2a. It is in pressure contact. For this reason, when used in an atmosphere where high and low temperatures are repeated, even when the protruding seal 10 is thermally expanded in a high temperature atmosphere, the thermal expansion is allowed in the accommodation space 12 and is fastened as in the conventional case. The thermal expansion of the protruding seal 10 is not restricted by the force.
In this case, as shown by the solid line in FIG. 5, the protruding seal 10 that has thermally expanded can be further curved by the protruding end 10 t side being displaced along the accommodating space constituting surface 12 s. As a result, it is possible to suppress the occurrence of “sagging” due to compression set as in the conventional case to the protruding seal 10 including the side surface (10a or 10b) constituting the protruding end 10t side as much as possible. In addition, the broken line in FIG. 5 has shown the accommodation state of the protruding seal | sticker 10 after heat shrink in a low-temperature atmosphere. FIG. 5 illustrates the specification of the protruding seal 10 in which one side surface 10b on the protruding end 10t side is in pressure contact with the housing space constituting surface 12s. On the contrary, although not particularly illustrated, the protruding end 10t Even in the specification of the protruding seal 10 in which the other side surface 10a on the side is in pressure contact with the housing space constituting surface 12s, it is possible to suppress the occurrence of “sagging” due to compression set as in the past as much as possible.

このように、突状シール１０の「ヘタリ」の発生防止が図られたシール構造によれば、高温と低温とが繰り返される雰囲気中での使用において、その突出端１０ｔ側を構成する側面（１０ａ又は１０ｂ）の収容空間構成面１２ｓに対する面圧を、従来のように低下させることなく、長期に亘って一定に維持することができる。これにより、ブーツ４とシャフト２ａとの間のシール性を長期に亘って維持することができ、グリース洩れの発生防止及び外部からの塵や水などの浸入防止を図ることができる。 Thus, according to the seal structure in which the occurrence of “sagging” of the projecting seal 10 is prevented, the side surface (10a) constituting the protruding end 10t side in use in an atmosphere where high and low temperatures are repeated. Alternatively, the surface pressure with respect to the housing space constituting surface 12s of 10b) can be kept constant over a long period of time without being lowered as in the prior art. Thereby, the sealing performance between the boot 4 and the shaft 2a can be maintained over a long period of time, and it is possible to prevent the occurrence of grease leakage and the entry of dust and water from the outside.

また、本実施の形態のシール構造によれば、ブーツ４の一連の製造プロセスで同時に突状シール１０を形成できると共に、収容空間１２はシャフト２ａの外周面２ｓを窪ませるだけで良い。これにより、従来よりも簡単に、かつ、低コストでシール構造を構築することができる。 Further, according to the seal structure of the present embodiment, the projecting seal 10 can be simultaneously formed by a series of manufacturing processes of the boot 4, and the accommodation space 12 only needs to be recessed on the outer peripheral surface 2s of the shaft 2a. Thereby, a seal structure can be constructed more easily and at a lower cost than in the past.

また、本発明は、上記した一実施の形態に限定されることはなく、以下のような変形例も本発明の技術範囲であり、同様の効果を実現することができる。なお、以下では、本変形例の特有の構成についての説明にとどめる。 Further, the present invention is not limited to the above-described embodiment, and the following modifications are also within the technical scope of the present invention, and the same effect can be realized. In the following description, only the specific configuration of this modification will be described.

図３(ａ),(ｂ)に示すように、本変形例に係るシール構造において、収容空間１２は、ブーツ４の小径側端部Ｐ１（バンド装着部６ｐ）の内周面Ｐｓに沿って周方向に連続して形成され、かつ、突状シール１０を含んだ所定範囲を所定量窪ませて形成されている。そして、上記一実施の形態で詳述した突状シール１０は、収容空間１２に沿って周方向に連続し、かつ、当該収容空間１２から内周面Ｐｓを越えて内向き（中心方向）に突出して形成されている。 As shown in FIGS. 3A and 3B, in the seal structure according to this modification, the accommodation space 12 is along the inner peripheral surface Ps of the small diameter side end portion P1 (band mounting portion 6p) of the boot 4. It is formed continuously in the circumferential direction, and a predetermined range including the protruding seal 10 is recessed by a predetermined amount. The protruding seal 10 described in detail in the above embodiment is continuous in the circumferential direction along the accommodation space 12 and inward (center direction) from the accommodation space 12 beyond the inner peripheral surface Ps. Protrusively formed.

本変形例において、収容空間１２は、小径側端部Ｐ１（バンド装着部６ｐ）の内周面Ｐｓよりも窪ませて形成した収容空間構成面１２ｓを有している。この場合、バンド締結状態において、収容空間構成面１２ｓとシャフト２ａの外周面２ｓとの間に、突状シール１０が弾性変形により湾曲して収容される収容空間１２が構成されることになる。なお、収容空間１２の大きさや形状は、上記一実施の形態と同様に構成できるため、その説明は省略する。 In the present modification, the accommodation space 12 has an accommodation space constituting surface 12s formed to be recessed from the inner peripheral surface Ps of the small diameter side end portion P1 (band mounting portion 6p). In this case, in the band fastening state, the accommodation space 12 in which the protruding seal 10 is curved and accommodated by elastic deformation is configured between the accommodation space constituting surface 12s and the outer peripheral surface 2s of the shaft 2a. In addition, since the size and shape of the accommodation space 12 can be configured in the same manner as in the above embodiment, the description thereof is omitted.

また、突状シール１０の突出長Ｈは、バンド締結状態において、突出端１０ｔ側を構成する側面（１０ａ又は１０ｂ）がシャフト２ａの外周面２ｓに当接して弾性変形により湾曲するとともに、弾性復元力により圧接して所定の面圧を維持できるような突出長Ｈに設定されている。なお、図３(ａ)には一例として、バンド締結状態において、突出端１０ｔ側の第２の側面１０ｂがシャフト２ａの外周面２ｓに当接して弾性変形により湾曲して圧接している状態が示されている。 Further, the protruding length H of the projecting seal 10 is such that, in the band fastening state, the side surface (10a or 10b) constituting the projecting end 10t side comes into contact with the outer peripheral surface 2s of the shaft 2a and is bent by elastic deformation, and elastically restored. The protrusion length H is set so as to maintain a predetermined surface pressure by pressure contact. As an example, FIG. 3A shows a state in which the second side surface 10b on the protruding end 10t side is in contact with the outer peripheral surface 2s of the shaft 2a and is curved and pressed by elastic deformation in the band fastening state. It is shown.

また、突状シール１０の突出方向は、図３(ｂ)には一例として、小径側端部Ｐ１（バンド装着部６ｐ）の内周面Ｐｓに垂直な方向に突出した突状シール１０が示されているが、これに限定されることはなく、例えばブーツ４の大径側端部Ｐ３側に向けて傾斜させても良いし、或いは、これとは反対側に向けて傾斜させても良い。図４(ｂ)には一例として、ブーツ４の大径側端部Ｐ３側に向けて傾斜させた突状シール１０が示されている。なお、突状シール１０の傾斜角度θは、上記一実施の形態と同様に構成できるため、その説明は省略する。 The protruding direction of the protruding seal 10 is shown in FIG. 3B as an example of the protruding seal 10 protruding in a direction perpendicular to the inner peripheral surface Ps of the small diameter side end portion P1 (band mounting portion 6p). However, the present invention is not limited to this. For example, the boot 4 may be inclined toward the large-diameter end P3, or may be inclined toward the opposite side. . FIG. 4B shows, as an example, a protruding seal 10 that is inclined toward the large-diameter end P3 side of the boot 4. In addition, since the inclination angle θ of the protruding seal 10 can be configured in the same manner as in the above-described embodiment, the description thereof is omitted.

ここで、本変形例に係るシール構造では、シャフト２ａは、その外周面２ｓを含めて一切何も加工を施すことなく、そのまま利用することができる。また、シャフト２への加工が不要な分だけシール構造を更に低コスト化することもできる。 Here, in the seal structure according to this modification, the shaft 2a can be used as it is without any processing including the outer peripheral surface 2s. In addition, the cost of the seal structure can be further reduced by the amount that processing on the shaft 2 is unnecessary.

また、本変形例では、突状シール１０及び収容空間１２から成るシール構造がブーツ４にのみ設けられており、ブーツ４単体としての発明とすることができる。そして、シャフト２ａの外周面２ｓの任意の部位にブーツ４の小径側端部Ｐ１を組み付けるだけで、突出端１０ｔ側の第２の側面１０ｂをシャフト２ａの外周面２ｓに対して弾性変形により湾曲して圧接するようにできる。これにより、シャフト２ａに対するブーツ４の小径側端部Ｐ１の組み付けの自由度を向上させることができる。この場合、上記一実施の形態で適用した位置決め手段を不要とすることができるため、その分だけシール構造を更に低コスト化することができる。 Moreover, in this modification, the seal structure which consists of the projecting seal 10 and the accommodation space 12 is provided only in the boot 4, and it can be set as the invention as the boot 4 single-piece | unit. Then, the second side surface 10b on the protruding end 10t side is curved by elastic deformation with respect to the outer peripheral surface 2s of the shaft 2a only by assembling the small diameter side end portion P1 of the boot 4 to an arbitrary portion of the outer peripheral surface 2s of the shaft 2a. And can be pressed. Thereby, the freedom degree of the assembly | attachment of the small diameter side edge part P1 of the boot 4 with respect to the shaft 2a can be improved. In this case, since the positioning means applied in the above-described embodiment can be eliminated, the cost of the seal structure can be further reduced.

また、上記一実施の形態及び変形例では、収容空間１２をシャフト２ａの外周面２ｓ又はブーツ４の小径側端部Ｐ１（バンド装着部６ｐ）の内周面Ｐｓのいずれか一方に構成した場合を想定して説明したが、これに限定されることはなく、双方に収容空間１２を設けるように構成しても良い。 Moreover, in the said one Embodiment and modification, when the accommodation space 12 is comprised in either one of the outer peripheral surface 2s of the shaft 2a, or the inner peripheral surface Ps of the small diameter side edge part P1 (band mounting part 6p) of the boot 4 However, the present invention is not limited to this, and the storage space 12 may be provided on both sides.

また、上記一実施の形態及び変形例では、ブーツ４の小径側端部Ｐ１（バンド装着部６ｐ）と等速ジョイント２のシャフト２ａとの間に構成されるシール構造について説明したが、これに限定されることはなく、当該シール構造を、ブーツ４の大径側端部Ｐ３（バンド装着部８ｐ）と等速ジョイント２のアウターケース２ｂとの間にも適用できることは言うまでもない。 In the embodiment and the modification described above, the seal structure configured between the small diameter side end portion P1 (band mounting portion 6p) of the boot 4 and the shaft 2a of the constant velocity joint 2 has been described. Needless to say, the seal structure can be applied between the large-diameter side end P3 (band mounting portion 8p) of the boot 4 and the outer case 2b of the constant velocity joint 2 without being limited.

また、上記一実施の形態及び変形例では、１つの突状シール１０と、これに対応した収容空間１２とから成る１つのシール構造を想定して説明したが、これに限定されることはなく、シール構造を２つ以上設けるようにしても良い。
さらに、シール構造を１つ（収容空間１２を１つ）とし、この収容空間１２に収容される突状シール１０を軸方向に複数設けるようにしても良い。 In the above-described embodiment and modification, the description has been made assuming a single seal structure including one projecting seal 10 and a storage space 12 corresponding thereto, but the present invention is not limited to this. Two or more seal structures may be provided.
Furthermore, one seal structure (one accommodating space 12) may be provided, and a plurality of protruding seals 10 accommodated in the accommodating space 12 may be provided in the axial direction.

(ａ)は、本発明の一実施の形態に係るシール構造が適用された等速ジョイント及び樹脂製ブーツの構成を示す図、(ｂ)は、小径側締結用バンドによって互いに締結された状態において、ブーツの小径側端部と等速ジョイントのシャフトとの間のシール構造の構成を一部拡大して示す断面図、(ｃ)は、収容空間が形成されたシャフトの外周面の構成を一部拡大して示す断面図、(ｄ)は、突状シールが形成された小径側端部の内周面の構成を一部拡大して示す断面図、(ｅ)は、同図(ｄ)に示された突状シールの構成を一部拡大して示す断面図。(a) is a figure which shows the structure of the constant velocity joint and resin boot to which the seal structure which concerns on one embodiment of this invention was applied, (b) in the state fastened mutually by the small diameter side fastening band FIG. 4 is a cross-sectional view showing a partially enlarged configuration of the seal structure between the small-diameter side end of the boot and the shaft of the constant velocity joint, and FIG. 5 (c) shows the configuration of the outer peripheral surface of the shaft in which the accommodation space is formed. FIG. 4D is a cross-sectional view showing an enlarged portion, FIG. 4D is a cross-sectional view showing a partially enlarged configuration of the inner peripheral surface of the small-diameter side end portion where the projecting seal is formed, and FIG. Sectional drawing which expands and shows a part of structure of the projecting seal shown by 2. 突状シールの先端側を構成する側面が収容空間の収容空間構成面に当接して弾性変形により湾曲して圧接した状態を一部拡大して示す断面図。Sectional drawing which expands partially and shows the state which the side surface which comprises the front end side of a projecting seal contact | abuts the accommodation space structural surface of accommodation space, and was curved and pressed by elastic deformation. (ａ)は、本発明の変形例に係るシール構造であって、小径側締結用バンドによって互いに締結された状態において、ブーツの小径側端部と等速ジョイントのシャフトとの間のシール構造の構成を一部拡大して示す断面図、(ｂ)は、収容空間及び突状シールが共に形成された小径側端部の内周面の構成を一部拡大して示す断面図。(a) is a seal structure according to a modified example of the present invention, in a state of being fastened together by a small-diameter side fastening band, the seal structure between the small-diameter side end of the boot and the shaft of the constant velocity joint. Sectional drawing which expands and shows a structure partially, (b) is a sectional view which expands and partially shows the structure of the internal peripheral surface of the small diameter side end part in which both the accommodation space and the projecting seal are formed. (ａ)は、本発明の一実施の形態に係るシール構造において、ブーツの大径側端部側に向けて傾斜させた突状シールの構成を一部拡大して示す断面図、(ｂ)は、本発明の変形例に係るシール構造において、ブーツの大径側端部側に向けて傾斜させた突状シールの構成を一部拡大して示す断面図。(a) is sectional drawing which expands partially and shows the structure of the projecting seal inclined toward the large diameter side edge part side of the boot in the seal structure which concerns on one embodiment of this invention, (b) These are sectional drawings which expand partially and show the structure of the projecting seal inclined toward the large-diameter side end part side of the boot in the seal structure according to the modification of the present invention. 高温と低温とが繰り返される雰囲気中において、突状シールが熱膨張及び熱収縮した際の変形状態を拡大して示す模式的な断面図。The typical sectional view which expands and shows the deformation state at the time of a projection seal thermally expanding and contracting in the atmosphere where high temperature and low temperature are repeated.

Explanation of symbols

２ａシャフト
２ｓシャフトの外周面
４樹脂製ブーツ
６小径側締結用バンド（締結部材）
６ｐバンド装着部（締結部材により締め付ける領域）
Ｐｓバンド装着部の内周面
１０突状シール
１２収容空間 2a Shaft 2s Shaft outer peripheral surface 4 Resin boot 6 Small diameter side fastening band (fastening member)
6p Band mounting part (area to be tightened by fastening member)
Inner circumferential surface 10 of Ps band mounting part Protruding seal 12 Accommodating space

Claims

In a state where the small diameter side end of the resin boot for constant velocity joint is fastened to the shaft of the constant velocity joint by a fastening member, the seal structure is configured between the small diameter side end and the shaft,
The small-diameter side end is provided with a projecting seal that is continuous in the circumferential direction along the inner peripheral surface of the region to be tightened by the fastening member, and protrudes in the center direction from the inner peripheral surface,
The outer peripheral surface of the shaft is provided with an accommodation space in which the protruding seal is curved and accommodated by elastic deformation in a state where the small diameter side end is fastened to the shaft by the fastening member,
The protruding seal is kept in pressure contact with the shaft and is not crushed by the fastening force of the fastening member, but is thermally expanded and heated in the housing space due to a change in the ambient temperature of the usage environment. Elastic deformation due to shrinkage is allowed,
A seal structure in which regions for fastening the inner peripheral surface of the small diameter side end portion to the outer peripheral surface of the shaft are provided on both sides in the axial direction of the housing space by the fastening member.

In a state where the small diameter side end of the resin boot for constant velocity joint is fastened to the shaft of the constant velocity joint by a fastening member, the seal structure is configured between the small diameter side end and the shaft ,
The small-diameter side end is provided with a projecting seal that is continuous in the circumferential direction along the inner peripheral surface of the region to be tightened by the fastening member, and protrudes in the center direction from the inner peripheral surface,
The inner circumferential surface of the small-diameter end is provided with an accommodation space in which the protruding seal is curved and accommodated by elastic deformation when the small-diameter end is fastened to the shaft by the fastening member. And
The protruding seal is kept in pressure contact with the shaft and is not crushed by the fastening force of the fastening member, but is thermally expanded and heated in the housing space due to a change in the ambient temperature of the usage environment. Elastic deformation due to shrinkage is allowed,
A seal structure in which regions for fastening the inner peripheral surface of the small diameter side end portion to the outer peripheral surface of the shaft are provided on both sides in the axial direction of the housing space by the fastening member.

In a state where the large diameter side end portion of the resin boot for a constant velocity joint is fastened by the fastening member to the outer case of the constant velocity joint, a sealing structure that consists between the outer case and the larger diameter end There,
The large-diameter side end is provided with a projecting seal that is continuous in the circumferential direction along the inner circumferential surface of the region to be tightened by the fastening member , and protrudes in the center direction from the inner circumferential surface,
Wherein the outer peripheral surface of the outer case, in a state in which the large diameter side end portion is fastened to the outer Kesu by the fastening member, wherein the projecting seal provided with housing space that will be accommodated in a curved by elastic deformation And
The projecting seal, the while maintaining the pressure contact state in the outer case, without being crushed by the fastening force of the fastening member, the thermal expansion in between the housing space due to a change in ambient temperature of the operating environment And elastic deformation due to heat shrinkage is allowed,
On both sides in the axial direction of the accommodating space, the sealing structure, wherein the area for clamping the inner peripheral surface of the larger diameter end to the outer peripheral surface of the front Symbol outer case by the fastening member is provided .

In a state where the large diameter side end portion of the resin boot for a constant velocity joint is fastened by the fastening member to the outer case of the constant velocity joint, a sealing structure that consists between the outer case and the larger diameter end There,
The large-diameter side end is provided with a projecting seal that is continuous in the circumferential direction along the inner circumferential surface of the region to be tightened by the fastening member , and protrudes in the center direction from the inner circumferential surface,
Wherein the inner peripheral surface of the large diameter side end portion, in a state in which the large diameter side end portion is fastened to the Autake over scan by said fastening member, yield of the projecting seal is housed in a curved by elastic deformation A space is provided,
The projecting seal, the while maintaining the pressure contact state in the outer case, without being crushed by the fastening force of the fastening member, the thermal expansion in between the housing space due to a change in ambient temperature of the operating environment And elastic deformation due to heat shrinkage is allowed,
On both sides in the axial direction of the accommodating space, the sealing structure, wherein the area for clamping the inner peripheral surface of the larger diameter end to the outer peripheral surface of the front Symbol outer case by the fastening member is provided .

The housing space is formed continuously in the circumferential direction along the outer peripheral surface of the shaft , and is formed by depressing a predetermined range including a region facing the protruding seal by a predetermined amount. The seal structure according to claim 1.

The accommodating space is formed continuously in the circumferential direction along the outer peripheral surface of the outer case , and is formed by depressing a predetermined range including a region facing the protruding seal by a predetermined amount. The seal structure according to claim 3, wherein the seal structure is characterized.

The accommodation space is formed continuously in the circumferential direction along the inner peripheral surface of the end portion on the small diameter side, and is formed by recessing a predetermined range including the protruding seal by a predetermined amount. The seal structure according to claim 2 .

The housing space is formed continuously in the circumferential direction along the inner peripheral surface of the end portion on the large diameter side, and is formed by depressing a predetermined range including the protruding seal by a predetermined amount. The seal structure according to claim 4 , wherein

The projecting seal is accommodated in the accommodating space when the small diameter side end is attached to the shaft. 3. A positioning means for positioning in a fixed state is provided. The seal structure according to any one of 5 and 7.