JP5396159B2 - Valve timing adjusting device seal and valve timing adjusting device - Google Patents

Description

  The present invention relates to a valve timing adjusting device for changing the opening and closing timing of an intake valve and an exhaust valve of an engine of an automobile or the like according to an operation situation, and a seal thereof.

  This type of valve timing adjustment device is provided in a drive transmission system between a crankshaft of an engine and a camshaft that drives an intake valve and an exhaust valve, and transmits a rotation from the vane rotor coupled to the camshaft and the crankshaft. And a shoe housing. The vane rotor is accommodated in the shoe housing so as to be relatively rotatable within a predetermined rotation angle, and the phase difference of the vane rotor with respect to the shoe housing is controlled by the hydraulic pressure supplied into the shoe housing (Patent Documents 1 and 2). .

  In the valve timing adjusting device described above, a seal made of resin or the like is attached to the shoe housing and the rotating sliding portion of the vane in order to prevent liquid leakage from the hydraulic chamber containing the vane of the vane rotor. Further, an elastic material such as a metal leaf spring, an elastomer, and rubber is incorporated into the seal groove together with the seal so as to exert a sealing effect by pressing the seal (Patent Document 3).

  However, in the case of a structure in which a seal and a leaf spring for pressing the seal are incorporated in the seal groove, automatic assembly is difficult because the seal and the leaf spring must be assembled while being assembled in the assembly process. In addition, since the seal and the leaf spring are separate, a failure may occur in which the leaf spring is detached after the seal and the leaf spring are set or the incorporation of the leaf spring is forgotten. Even if a defect occurs, it cannot be visually confirmed whether or not the leaf spring is incorporated if the seal is incorporated. Therefore, in the final assembly process, it is not possible to find a defect unless a functional evaluation is performed, and the inspection takes time. Furthermore, in the case where an elastic material such as elastomer or rubber is bonded to the seal, it is difficult to confirm the appearance even if there is poor adhesion, so that a defective product may be mistakenly incorporated.

  In order to solve such a problem, there is also known a seal in which a seal portion and a spring portion provided on the surface opposite to the seal surface are integrally formed of resin (Patent Document 4).

Japanese Patent No. 3711872 JP 09-324611 A JP 2000-038909 A JP 2000-265814 A

  The seal part and the spring part integrally formed of resin have an advantage that they are excellent in assemblability and can be automatically assembled. However, since a resin having excellent sealing performance is selected as the resin, there is no problem in the sealing function of the sealing portion, but the spring portion gradually becomes permanently deformed with the passage of the service period, and the elastic force is reduced. For this reason, the force which presses a seal | sticker part to a counterpart member falls, and there exists a possibility that sealing performance may be impaired.

  Accordingly, the present invention provides a highly reliable seal for a valve timing adjusting device, which has no possibility of erroneously incorporating a defective product, is excellent in assemblability, can be automatically assembled, and can maintain seal performance even after long-term use. It is an object of the present invention to provide a valve timing adjusting device using the seal.

  In order to solve the above-mentioned problems, an invention relating to a seal for a valve timing adjusting device is mounted in a seal groove of a rotational sliding portion between a shoe housing and a vane rotor of the device, and the seal has a low friction. And a rubber elastic member that presses the seal surface of the seal member against the mating member with a desired pressure contact force, and the elastic member is on the opposite side of the seal surface to the seal member. The surface is combined and integrated by a concave-convex fitting structure.

  In order to solve the above-mentioned problems, an invention relating to a valve timing adjusting device includes a vane rotor, a shoe housing in which a hydraulic chamber is provided in which the vane rotor is rotatably accommodated within a predetermined angle range, and the liquid A hydraulic passage for adjusting the phase difference of the vane rotor with respect to the shoe housing by supplying and discharging hydraulic fluid to and from the pressure chamber, and an engine crankshaft and / or an intake valve and / or an exhaust valve of the engine. In the valve timing adjusting device for an engine, which is provided between a camshaft to be driven and the shoe housing rotates together with one of the two shafts and the vane rotor rotates together with the other shaft, the shoe housing and the vane rotor The seal attached to the rotating sliding part A seal member made of a low friction material and a rubber elastic member that presses the seal surface of the seal member against a mating member with a desired pressure contact force, and the elastic member is opposite to the seal surface of the seal member This is one that is combined and integrated by the concave-convex fitting structure on the surface.

  In the valve timing adjustment device seal according to the present invention, the seal member and the elastic member made of rubber are configured as separate parts. Therefore, materials for the seal member and the elastic member can be selected according to the respective characteristics. . In the present invention, since the elastic member can be formed of rubber having sufficient durability, a stable elastic force can be applied to the seal member over a long period of time. Further, since the elastic member is coupled to the seal member by the concave-convex fitting structure, it is possible to automate the coupling operation of both members. In addition, since the elastic force of the elastic member itself acts on the fitting portion so as to be reliably integrated, the possibility of the occurrence of a defect that the elastic member is missing in the assembling process is eliminated. Further, since it is reliably integrated without using an adhesive, there is no problem of poor adhesion.

  The concave-convex fitting structure can obtain a strong coupling force by adopting a configuration in which a constriction is formed at the base of the convex portion and a constriction is formed in the opening of the concave portion to engage with the constricted portion. In addition, since the elastic member is elastically deformed when the concave and convex are fitted, it can be easily fitted.

  Furthermore, when the structure which provided the some leg part to the elastic member is taken, it becomes easy to carry out an elastic deformation and there exists an effect which the sealing effect increases further.

These are sectional drawings of an embodiment. These are sectional drawings of the YY line of FIG. (A) is an enlarged cross-sectional view of a seal mounting portion, (b) is a bottom view of the seal, (c) is a cross-sectional view taken along line cc of (a), and (d) is an exploded view of the seal. It is sectional drawing. (A) is an enlarged cross-sectional view of another seal mounting part, (b) is a bottom view of the seal, (c) is a cross-sectional view taken along line cc of (a), and (d) is a seal. FIG.

  An embodiment of the present invention will be described below with reference to the accompanying drawings. As shown in FIGS. 1 and 2, the valve timing adjusting device for an engine according to the present invention includes a vane rotor 11, a shoe housing 12 that accommodates the vane rotor 11 so as to be relatively rotatable within a predetermined angle range, and the shoe housing. 12 and a driven member 14 coupled to the vane rotor 11 coaxially.

  By fitting a fitting convex portion 15 protruding in the axial direction at the tip of the driven member 14 into a fitting concave portion 16 provided at the center of the vane rotor 11, the vane rotor 11 and the driven member 14 are fitted. Are connected in a coaxial state. The bolt 17 is inserted into the fitting convex portion 15 from the center of the outer end surface of the boss portion 20 of the vane rotor 11, and the bolt 17 is screwed to the driven member 14, thereby integrating the vane rotor 11 and the driven member 14. ing.

  The driven member 14 is integrally provided by extending one end portion of an engine camshaft 18. A flange portion 19 is formed at an intermediate portion from one end portion of the camshaft 18 to the tip of the driven member 14, and a journal portion 21 supported by the engine block is between the camshaft 18 and the flange portion 19. . A support portion 22 extends from the flange portion 19 to the distal end. The drive member 13 is disposed on the flange portion 19 side in the support portion 22, and comes into contact with the drive member 13 on the distal end side of the shoe housing 12. The annular inner plates 23 are supported so as to be relatively rotatable. The camshaft 18 opens and closes either or both of an intake valve and an exhaust valve (not shown) of the engine.

  The shoe housing 12 includes a housing body 24 that surrounds the outer periphery of the vane rotor 11, the inner plate 23 that is applied to the inner end surface (the surface on the camshaft 18 side), and an annular outer plate that is applied to the opposite outer end surface. 25. Four shoes 26 are provided on the inner diameter surface of the housing main body 24 so as to protrude radially inward at regular intervals in the circumferential direction (see FIG. 2). The inner peripheral surface 55 of each shoe 26 is in sliding contact with the outer diameter surface of the boss portion 20 of the vane rotor 11 via a shoe-side seal 30, and a fan-shaped hydraulic pressure chamber 29 is formed between the adjacent shoes 26.

  As shown in FIG. 1, bolts 27 are inserted through the outer plate 25, the shoe 26 and the inner plate 23 of the shoe housing 12 at the four portions of the shoe 26. Screwed together. Thereby, the drive member 13 and the shoe housing 12 are integrated. A gear 13a is formed on the outer diameter surface of the drive member 13, and the drive member 13 is interlocked with the crankshaft through a transmission mechanism such as a crankshaft of the engine and a gear train.

  The housing body 24 is made of a heat-resistant synthetic resin or a metal such as a lightweight alloy. The inner plate 23 and the outer plate 25 may be made of a metal such as a lightweight alloy, or may be made of a heat-resistant synthetic resin like the housing body 24.

  As described above, the drive member 13 and the shoe housing 12 are integrated, and the driven member 14 and the vane rotor 11 are integrated. As a result, the driven member 14 can rotate relative to the driving member 13 within a certain angular range regulated by the hydraulic chamber 29.

  The driving member 13 and the driven member 14 rotate in the clockwise direction when viewed from the X direction indicated by an arrow in FIG. Hereinafter, this rotational direction is referred to as an advance direction.

  As shown in FIG. 2, vanes 28 are provided at regular intervals at four locations in the circumferential direction of the outer diameter surface of the boss portion 20 of the vane rotor 11. Each vane 28 is housed in each hydraulic chamber 29 of the shoe housing 12 and can rotate relative to the shoe housing 12 within a certain range limited in the circumferential direction inside each hydraulic chamber 29. Yes.

  The axial surfaces of the vanes 28 are slidably rotated while being in close contact with the inner surfaces of the inner plate 23 and the outer plate 25 of the shoe housing 12. Further, the outer peripheral surface 56 of each vane 28 slides and rotates on the inner diameter surface of the hydraulic chamber 29 via the vane side seal 40. Thereby, each hydraulic pressure chamber 29 is divided into a retarded hydraulic pressure chamber 29a which is a relatively delayed position when viewed in the advanced angle direction, and an advanced hydraulic pressure chamber 29b which is an advanced position. The material of the vane rotor 11 is also made of a heat-resistant synthetic resin or a metal such as a lightweight alloy.

  Among the four vanes 28, a rotation lock mechanism 31 that locks the relative rotation of the vane rotor 11 and the shoe housing 12 is provided in one vane 28. In the rotation lock mechanism 31, a lock pin 33 is slidably incorporated in a storage hole 32 that penetrates the vane 28 in the axial direction, and the tip of the lock pin 33 faces the inner plate 23 so as to face the storage hole 32. A lock hole 34 into which the part is inserted is provided.

  As shown in FIG. 2, the lock hole 34 matches the storage hole 32 when the vane 28 is in contact with one shoe 26, that is, at the most retarded position, and the tip of the lock pin 33 is aligned. It is provided at the position to be inserted. A biasing spring 35 is stored between one end of the storage hole 32 and the lock pin 33 (see FIG. 1), and the lock pin 33 is biased in the direction of the lock hole 34 by the biasing spring 35. Further, a hydraulic chamber 37 is provided between the outer peripheral flange 36 of the lock pin 33 and the storage hole 32.

  The driven member 14 is provided with two systems of liquid passages 41 and 42, and a pump for supplying and discharging hydraulic fluid from an opening provided in the journal portion 21 through an external liquid passage (not shown) and a control valve, respectively. Leads to drain. One liquid passage 41 communicates with an annular small-diameter liquid passage 43 provided in the boss portion 20 of the vane rotor 11, and the other liquid passage 42 communicates with an annular large-diameter liquid passage 44. The small-diameter liquid passage 43 communicates with each retarded hydraulic pressure chamber 29a via the branch liquid passage 45 (see FIG. 2), and the large-diameter liquid passage 44 communicates with each advanced-angle hydraulic pressure chamber 29b via the branch liquid passage 46. Is done. Further, the hydraulic chamber 37 and the lock hole 34 of the rotation lock mechanism 31 communicate with the liquid passages 41 and 42, respectively.

  Next, the shoe side seal 30 and the vane side seal 40 will be described with reference to FIG. Since these seals 30 and 40 have the same structure, the shoe-side seal 30 will be mainly described with reference to the same drawing, and portions related to the vane-side seal 40 are shown in parentheses. The shoe-side seal 30 and the vane-side seal 40 may have different sizes.

  As shown in the figure, the shoe side seal 30 (vane side seal 40) includes a seal member 51 made of a low friction material and a rubber elastic member 52. The length of the seal member 51 in the axial direction is the rotational sliding portion of the shoe 26 (vane 28) (the inner peripheral surface 55 of the shoe 26 in the case of the shoe-side seal 30 and the outer peripheral surface 56 of the vane 28 in the case of the vane-side seal 40). ) And the length of the seal groove 53 opened in both ends in the axial direction. Further, the width matches the groove width of the seal groove 53. A surface that slightly rises from the inner peripheral surface 55 (outer peripheral surface 56) is a seal surface 54, and this seal surface 54 is pressed against a mating member to perform sealing.

  A portion having a constant thickness a including the seal surface 54 (see FIG. 3D) constitutes a seal portion 57. Further, on the lower surface of the seal portion 57 (surface opposite to the seal surface 54), a connecting portion 58 having a thickness b that is narrower than the seal portion 57 by a certain width c is integrally provided on its four sides. A groove-like recess 59 is provided over the entire length in the center in the width direction of the lower surface of the connecting portion 58. A narrowed portion 60 is provided in the opening of the recess 59.

  The elastic member 52 has an upper surface that coincides with the lower surface of the seal portion 57, and is provided with a ridge-shaped convex portion 61 over the entire length in the center in the width direction of the upper surface. A plurality of legs 63 are provided on the lower surface.

  A constricted portion 62 that matches the cross-sectional shape of the narrowed portion 60 of the concave portion 59 is provided at the base portion of the convex portion 61. On the opposite surface, two rows of fin-shaped leg portions 63 are provided in two rows each having slits at intervals d (see FIG. 3B) in the longitudinal direction. . Each leg portion 63 is disposed at a diagonal position on the lower surface of the rectangular shape of the elastic member 52.

  The sealing member 51 and the elastic member 52 are integrally connected by a concave-convex fitting structure in which the convex portion 61 of the elastic member 52 is elastically deformed and forcibly fitted into the concave portion 59 of the sealing member 51 (FIG. 3). (See (c)). In particular, a strong connection state can be maintained for a long time by the engagement structure between the constricted portion 62 of the convex portion 61 and the narrowed portion 60 of the concave portion 59 and the elastic force of the elastic member 52.

  Another example of the shoe-side seal 30 (vane-side seal 40) shown in FIG. 4 is that the convex portion 64 is provided on the lower surface of the seal member 51, the concave portion 66 is provided on the elastic member 52 side, and the leg portion 63 is provided. The difference is that two dot-shaped leg portions 63 in two rows in the longitudinal direction and four rows in each row are provided in eight locations. The constricted portion 65 is provided in the convex portion 64 and the constricted portion 67 is provided in the concave portion 66, and the concave portion 66 is elastically deformed, and is integrally connected by the concave and convex fitting structure that is forcedly fitted to the convex portion 64. (See FIG. 4 (c)).

  Also in this case, the strong connection state can be maintained for a long time by the engagement between the constricted portion 65 of the convex portion 64 and the narrowed portion 67 of the concave portion 66.

  3 and 4, the rubber elastic member 52 causes the sealing surface 54 of the sealing member to be a mating member (in the case of the shoe side seal 30, the outer diameter surface of the boss portion 20 of the vane rotor 11, the vane side). In the case of the seal 40, a desired pressure contact force is applied to the inner diameter surface of the housing body 24. In addition, a space having a width c is generated between the elastic member 52 and both inner wall surfaces of the seal groove 53 in a state of being mounted in the seal groove 53, and there is also a space between the leg portions 63. Allows free elastic deformation.

  Each of the sealing members 51 may be any low-friction material having oil resistance that does not swell with respect to the working oil. For synthetic resins, polyphenylene sulfide (PPS) resin, polyether ether ketone (PEEK) resin, polyamide Engineering plastics such as resin, polytetrafluoroethylene resin and polyacetal resin can be used. In particular, PPS and PEEK are preferable because they are excellent in heat resistance and low friction characteristics. In addition to synthetic resins, copper-based and aluminum-based sintered alloys can be used.

The rubber material used for each of the elastic members 52 can be any material having oil resistance that does not swell with respect to the hydraulic oil, and silicone rubber, fluorine rubber, nitrile rubber, and acrylic rubber are highly reliable. preferable. If the rubber hardness of the rubber material is in the range of 50 to 90 , it is preferable because the seal member 51 can be pressed against the mating sliding surface with an appropriate pressing force. Rubber hardness is there is a case 5 0 not Mitsurude is the pressing force is not enough, there is a case in which 9 0 good Ri high, the pressing force is too high. If it is in the range of 50 to 90, it is easy to calculate the pressing force by design.

  It is desirable that the seal member 51 and the elastic member 52 are not bonded by an adhesive but integrated only by an elastic force. This is because, when an adhesive is used, when adhesion failure occurs, it is difficult to separate from the appearance.

Next, the operation of the valve timing adjusting device described above will be described. When the engine is stopped, since the pump is also stopped, the hydraulic fluid is not supplied to the liquid passages 41 and 42. As shown in FIG. 2, the vane rotor 11 is in the most retarded position, and the lock pin 33 of the rotation lock mechanism 31 is pushed by the spring force of the urging spring 35, and its tip is inserted into the lock hole 34. The Accordingly, the vane rotor 11 is locked with respect to the shoe housing 12. Even engine been started, and remains locked until the liquid pressure reaches or exceeds a certain, to eliminate the risk of the vane rotor 11 by the fluctuation torque acting on the cam shaft 18 impinges on the fluid pressure chamber 29 of Shuhaujin grayed 12 ing.

  Until the lock is released, the camshaft 18 is connected to the shoe housing 12 via the drive member 13 interlocking with the crankshaft, the shoe housing 12 integral with the drive member 13, and the vane rotor 11 locked to the shoe housing 12. On the other hand, it rotates with the most retarded phase difference.

When the engine is in a steady state, the hydraulic fluid controlled by the control valve is supplied to the rotation lock mechanism 31 through the respective fluid passages 41 and 42, so that the lock pin 33 compresses the urging spring 35 and moves backward. The lock is released. Also, advances since the liquid pressure on the corner hydraulic chamber 29b and the retard hydraulic chamber 29a at a predetermined ratio of Ru is supplied, the vane rotor 11 and integral therewith a cam shaft 18 is rotated in the advance direction, advance fluid pressure The chamber 29b and the retarded hydraulic pressure chamber 29a are stopped at a point where the hydraulic pressures are balanced, and a constant advance angle phase difference is applied to the camshaft 18 with respect to the crankshaft. The magnitude of this phase difference, the control of the control valve, the opening and closing timings of the liquid defined et al is the magnitude of the fluid pressure supplied to the passage 41, the intake valve or the exhaust valve by the cam mounted on the cam shaft 18 Is adjusted.

  When the engine is stopped, the vane rotor 11 is always controlled to return to the most retarded position, and the vane rotor 11 is locked by the spring force of the urging spring 35 acting on the lock pin 33.

  In the above description, the shoe housing 12 and the drive member 13 are configured as separate members. However, both can be configured as an integral part. Further, the functions of the driving member 13 and the driven member 14 are exchanged so that the driven member 14 bears the function of the driving member, and the driving member 13 is caused to bear the function of the driven member. A configuration in which the camshaft 18 is interlocked can also be adopted.

  In the valve timing adjusting device having the above-described configuration and operation, the shoe side seal 30 attached to the shoe 26 and the vane side seal 40 attached to the vane 28 cause liquid leakage in the hydraulic chambers 29a and 29b. To prevent and enable stable valve timing adjustment.

  Since the seal 30 (40) has a structure in which the seal member 51 and the rubber elastic member 52 are integrated with each other by elastic concave / convex fitting, the elastic member 52 is attached to the seal member 51. It is securely attached by its own elastic force, so that there will be no poor assembly.

  In the case of the embodiment shown in FIG. 3, since the convex portion 61 of the elastic member 52 is fitted into the concave portion 59 of the seal member 51, the incorporation of the elastic member 52 with respect to the seal member 51 is ensured. Become.

  In the case of the embodiment shown in FIG. 4, the convex portion 64 having the constricted portion 65 of the seal member 51 is provided, the constricted portion 67 is provided in the concave portion 66 of the elastic member 52, and the constricted portion 67 is engaged with the constricted portion 65. Therefore, the assembling property of the elastic member 52 with respect to the seal member 51 is ensured and the assembling workability is improved.

  In any of the above cases, the elastic member 52 is made of rubber having a rubber hardness of 50 to 90, so that it does not come off the seal member 51 after the elastic member 52 is assembled. Since the rubber is silicone rubber, fluorine rubber, nitrile rubber, or acrylic rubber, the oil resistance is sufficient with respect to the hydraulic oil, and the pressing force of the seal does not decrease. Since the low friction material which is the seal member 51 is a synthetic resin, the sliding mating surface is not damaged, it is possible to contribute to weight reduction, and manufacture is facilitated.

  Since the synthetic resin as the seal member 51 is either PPS or PEEK, it becomes an excellent seal member having excellent low friction characteristics, heat resistance, and oil resistance. When a sintered alloy is used as the low friction material constituting the seal member 51, the linear expansion coefficient can be made the same as that of the shoe housing 12 and the vane rotor 11, so that the sealability does not change due to temperature change and is easy to manufacture. It is.

  Further, since the plurality of leg portions 63 are formed on the elastic member 52, the seal 30 (40) can be stably held in the seal groove 53. Since the leg portions 63 are arranged in two rows in the longitudinal direction, the seal 30 (40) can be stably held in the seal groove 53. When the leg portion 63 has a dot shape as shown in FIG. 4, the pressing force of the seal member 51 can be made uniform.

  Moreover, when the leg part 63 is a fin shape as shown in FIG. 3, the pressing force of the seal member 51 can be made uniform. This is particularly advantageous for the seal member 51 having a relatively long longitudinal direction. As shown in FIG. 3, when the leg part 63 is formed in a diagonal position, the seal 30 (40) can be stably held in the seal groove 53, and the sealing performance is stabilized. In the case of FIG. 3, since the distance d between the two rows of leg portions 63 is a slit, the pressing force of the elastic member 52 can be applied in shape.

  In the valve timing adjusting device of the present invention equipped with the seal 30 (40) as described above, the reliability of the valve timing adjusting function is improved because the seal 30 (40) has high performance.

DESCRIPTION OF SYMBOLS 11 Vane rotor 12 Shoe housing 13 Drive member 13a Gear 14 Driven member 15 Fitting convex part 16 Fitting concave part 17 Bolt 18 Camshaft 19 ridge part 20 Boss part 21 Journal part 22 Support part 23 Inner board 24 Housing main body 25 Outer board 26 Shoe 27 Bolt 28 Vane 29 Hydraulic chamber 29a Slow hydraulic chamber 29b Advanced hydraulic chamber 30 Shoe side seal 31 Rotation lock mechanism 32 Storage hole 33 Lock pin 34 Lock hole 35 Energizing spring 36 Outer flange 37 Hydraulic chamber 40 Vane side seal 41, 42 Liquid passage 43 Small diameter liquid passage 44 Large diameter liquid passage 45, 46 Branch liquid passage 47, 48 Unlock liquid passage 51 Seal member 52 Elastic member 53 Seal groove 54 Seal surface 55 Inner peripheral surface 56 Outer peripheral surface 57 Sealing part 58 Connecting part 59 Recessed part 60 Narrow part 61 Part 62 constricted portion 63 leg 64 projecting portion 65 constricted portion 66 recess 67 constriction

Claims (13)

In a seal for a valve timing adjusting device mounted in a seal groove of a rotational sliding portion between a shoe housing and a vane rotor of the valve timing adjusting device, the seal is a seal member made of a low friction material and a seal surface of the seal member. A rubber elastic member having a rubber hardness of 50 to 90 pressed against the member with a desired pressure contact force, and the elastic member has an upper surface that matches a surface opposite to the seal surface with respect to the seal member. A valve timing adjusting device seal characterized in that the seal member has a concave-convex fitting structure and is integrated with the seal member, and the connection with the seal member is maintained by the elastic force of the elastic member .   The concave-convex fitting structure is configured by fitting a concave portion provided on a surface opposite to the sealing surface of the seal member and a convex portion provided on the elastic member, and the concave portion is narrowed at an opening end thereof. The valve timing adjusting device seal according to claim 1, wherein the convex portion has a constricted portion that engages with the narrowed portion at a base thereof.   The concave / convex fitting structure is configured by fitting a convex portion provided on a surface opposite to the sealing surface of the seal member and a concave portion provided on the elastic member, and the convex portion is constricted at a base thereof. 2. The valve timing adjusting device seal according to claim 1, wherein the concave portion has a constricted portion engaged with the constricted portion at an opening end thereof. 4. The valve timing adjusting device seal according to claim 1, wherein the rubber is any one of silicone rubber, fluorine rubber, nitrile rubber, and acrylic rubber. 5. The valve timing adjusting device seal according to any one of claims 1 to 4 , wherein the low friction material is a synthetic resin. 6. The valve timing adjusting device seal according to claim 5 , wherein the synthetic resin is either a polyphenylene sulfide resin or a polyether ether ketone resin. The valve timing adjusting device seal according to any one of claims 1 to 4 , wherein the low friction material is a sintered alloy.
The valve timing adjustment device seal according to any one of claims 1 to 7 , wherein the elastic member has a plurality of legs formed on a surface of the seal groove facing the groove bottom.   9. The valve timing adjusting device seal according to claim 8, wherein the leg portions are arranged in two rows in the longitudinal direction. The valve timing adjustment device seal according to claim 8 or 9 , wherein the leg portion has a dot shape. The valve timing adjustment device seal according to claim 8 or 9 , wherein the leg portion has a fin shape.
The valve timing adjusting device seal according to any one of claims 1 to 11 , wherein the elastic force of the elastic member contributes to the coupling force of the concave-convex fitting structure. A shoe rotor in which a vane rotor, a hydraulic pressure chamber that accommodates the vane rotor so as to be relatively rotatable within a predetermined angle range, and a hydraulic fluid is supplied to and discharged from the hydraulic pressure chamber so that a phase difference of the vane rotor with respect to the shoe housing is obtained. A fluid passage for adjusting, provided between the crankshaft of the engine and a camshaft that drives either or both of the intake valve and the exhaust valve of the engine, and one of the shafts In the valve timing adjusting device in which the shoe housing rotates together with the other shaft and the vane rotor rotates, the seal attached to the rotating sliding portion between the shoe housing and the vane rotor is any one of claims 1 to 12. Valve timing adjusting device characterized in that the seal is described

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