VALVE OPENING/CLOSING TIMING CONTROL DEVICE

Abstract

A valve opening/closing timing control device includes a driving rotary body rotatable in synchronism with a crankshaft of an internal combustion engine, a driven rotary body rotatable in unison with a cam shaft of the internal combustion engine and rotatable also relative to the driving rotary body within this driving rotary body, a fluid pressure chamber formed by the driving rotary body and the driven rotary body, and a partitioning portion that partitions the fluid pressure chamber into an advance chamber and a retard chamber. The driving rotary body includes an aluminum housing having a pulley that receives a drive force of the crankshaft via a drive belt and a plate attached to at least one face of the housing. Between the housing and the plate, there is provided a gap allowing outflow of fluid.

Claims

1. A valve opening/closing control device comprising: a driving rotary body rotatable in synchronism with a crankshaft of an internal combustion engine and rotatable also about a rotational axis; a driven rotary body rotatable in unison with a cam shaft of the internal combustion engine about the rotational axis and rotatable also relative to the driving rotary body within this driving rotary body; a fluid pressure chamber formed by the driving rotary body and the driven rotary body; a partitioning portion provided within the fluid pressure chamber for partitioning the fluid pressure chamber into a retard chamber and an advance chamber allowing introduction and discharge of fluid thereto/therefrom, the partitioning portion selectively displacing relative rotation phase of the driven rotary body relative to the driving rotary body in a retard direction in which capacity inside the retard chamber is increased in association with introduction of the fluid or an advance direction in which capacity inside the advance chamber is increased in association with introduction of the fluid; the driving rotary body including an aluminum housing having a pulley that inputs drive force from the crankshaft via a drive belt and a plate attached to at least one face of the housing extending along the rotational axis; and a gap allowing outflow of the fluid therethrough being provided between the housing and the plate.

2. The valve opening/closing control device of claim 1, wherein the pulley is subjected to an alumite treatment in advance.

3. The valve opening/closing control device of claim 1, wherein at least one of a contacting face of the housing and a contacting face of the plate is provided as an alumite-treated surface having a predetermined surface roughness; and the contacting face of the housing and the contacting face of the plate are placed in direct contact with each other.

4. The valve opening/closing control device of claim 1, wherein: the partitioning portion is provided in the driven rotary body; the housing includes a cylindrical wall portion having, in its inner circumferential face, a sliding contacting area where the housing comes into sliding contact with the partitioning portion; between the pulley and the cylindrical wall portion, there is formed a groove portion that penetrates in the direction of the rotational axis and extends in a circumferential direction relative to the rotational axis; and the groove portion and the sliding contacting area have a mutually overlapped area in a radial direction of the rotational axis.

5. The valve opening/closing control device of claim 4, wherein a width of the groove portion along the radial direction of the rotational axis is set greater than a width of the contacting face of the housing that comes into contact with the plate along the radial direction.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0033] FIG. 1 is a side view in section of a valve opening/closing timing control device according to an embodiment,

[0034] FIG. 2 is a plane view in section of the valve opening/closing timing control device according to the embodiment, and

[0035] FIG. 3 is an exploded perspective view of a driving rotary body in the embodiment.

EMBODIMENTS

[0036] [General Configuration]

[0037] Next, an embodiment of the present invention will be explained with reference to the accompanying drawings.

[0038] A valve opening/closing timing control device relating to this embodiment is shown in FIGS. 1 through 3. FIG. 1 is a side view in section of the inventive device. FIG. 2 is a plane view in section of the same and FIG. 3 is an exploded perspective view of a driving rotary body.

[0039] The valve opening/closing timing control device consists mainly of a driving rotary body A (an outer rotor) rotatable in synchronism with a crankshaft Z of an internal combustion engine and rotatable also about a rotational axis X, a driven rotary body B (an inner rotor) mounted within the driving rotary body A and rotatable in unison with a cam shaft C of the internal combustion engine about the rotational axis X, and a phase control section for adjusting a relative rotation phase between the driving rotary body A and the driven rotary body B.

[0040] Between the driving rotary body A and the driven rotary body B, a fluid pressure chamber R is formed. A first protruding portion 1 protruding inwards from the driving rotary body A on the outer side comes into contact with an outer circumferential face B1 of the driven rotary body B disposed on the inner side; and a second protruding portion 2 protruding from the outer circumferential face B1 of the driven rotary body B comes into contact with an inner circumferential face W1 of the driving rotary body A. These first protruding portion 1 and second protruding portion 2 function as partitioning portions of the fluid pressure chamber R and partition the fluid pressure chamber R into an advance chamber R1 and a retard chamber R2.

[0041] In operation, when operating fluid is fed to the advance chamber R1 via an advance oil passage 3 and operating fluid is discharged from the retard chamber R2 via a retard oil passage 4, the driven rotary body B is relatively rotated in the clockwise direction in FIG. 2. As a result, the valve opening/closing timing of the internal combustion engine is advanced. For instance, such an advance operation as above is effected for e.g. increasing the rotational speed of the internal combustion engine. On the other hand, when the operating fluid is fed to the retard chamber R2 and the operating fluid is discharged from the advance chamber R1, the driven rotary body B is relatively rotated in the counterclockwise direction in FIG. 2. As a result, the valve opening/closing timing of the internal combustion engine is retarded (delayed). This latter operation is effected for e.g. decreasing the rotational speed of the internal combustion engine, and an operation with idling rotation will be effected in a most retarded phase.

[0042] [Housing]

[0043] In this embodiment, a housing H of the driving rotary body A is formed of an aluminum material. This driving rotary body A consists mainly of three components; namely, the housing H integrally forming a pulley P in its outer circumferential portion, a front plate FP and a rear plate RP which sandwich this housing H from the opposed sides thereof. These components are assembled together with using a plurality of fastening bolts 5. The housing H, as shown in FIG. 3, has a substantially constant cross sectional shape as seen in a section along the fastening direction and is produced by extrusion molding of the aluminum material. Incidentally, as an alternative arrangement to the above, it is possible to mold the front plate FP or the rear plate RP integrally with the housing H. In such case, the production can be made by e.g. die-casting technique.

[0044] In particular, the housing H includes the pulley P formed on the outer circumferential side and a cylindrical wall portion W formed on its inner circumferential side and accommodating the driven rotary body B. This cylindrical wall portion W includes an inner circumferential face W1 which comes into sliding contact with the second protruding portion 2 formed in the driven rotary body B. Further, the cylindrical wall portion W includes a plurality of first protruding portions 1 which come into sliding contact with the outer circumferential face B1 of the driven rotary body B.

[0045] As shown in FIG. 2, on the outer circumferential side of the cylindrical wall portion W, the pulley P is integrally formed in such a manner that most of it is spaced from the cylindrical wall portion W. The cylindrical wall portion W and the pulley P are connected at connecting portions 6 provided at same positions as the first protruding portions 1 provided at four positions in distribution along the circumferential direction.

[0046] With the above-described arrangement of the cylindrical wall portion W and the pulley P being assembled and formed integrally with each other, in comparison with an arrangement of these two parts being provided separately and connected as such to each other, the above arrangement advantageously eliminates trouble of an alignment operation for them. Further, the arrangement eliminates also the fastening bolts 5 for integrating them together and the fastening operation per se too can be eliminated. Thus, such advantages as weight reduction and cost reduction can be achieved.

[0047] [Bolt Fastening]

[0048] As shown in FIG. 2 and FIG. 3, a bolt hole 7 formed in the housing H for allowing insertion of the fastening bolt 5 is provided at a center position of the respective first protruding portion 1. With this arrangement, it is possible to secure a large contact area between the front plate FP or the rear plate RP and the housing H and to avoid application of locally concentrated load to the housing H at the time of fastening of the fastening bolt 5. Consequently, the arrangement can lessen the possibility of deforming of the front plate FP, the rear plate RP and the housing H. Thus, it becomes possible to prevent unnecessary leakage of the operating fluid held within the fluid pressure chamber R to the outside from e.g. a gap between the front plate FP and the housing H.

[0049] Incidentally, the front plate FP and the rear plate RP too can be formed of aluminum material. In the case of such arrangement, the driving rotary body A can be formed further light-weighted. Incidentally, in case the rear plate RP is formed of aluminum material, a female thread portion 8 to which the fastening bolt 5 engages can be formed slightly longer, so as to prevent damage of this female thread portion 8 by the fastening force.

[0050] Also, the position of the female thread portion 8 is a position between the first protruding portion 1 and the connecting portion 6 along the radial direction. More specifically, this is a position slightly offset toward the first protruding portion 1. With this position setting, when the second protruding portion 2 of the driven rotary body B reaches the most advanced phase and the most retarded phase to come into contact with the first protruding portion 1, bending deformation of the first protruding portion 1 can be avoided. Incidentally, in the case of the example shown in FIG. 2, the arrangement is made such that only the second protruding portion 2 located at the left upper side in FIG. 2 will come into contact with the first protruding portion 1.

[0051] [Alumite Treatment]

[0052] In case the pulley P and the housing H of the driving rotary body A are formed of aluminum material which is a relatively soft material, frictional wear tends to occur in the pulley P due to its friction with the drive belt V. Then, for this driving rotary body A, in order to enhance the hardness of its surface, an anodizing oxidization treatment, alias, an alumite treatment, is effected. Specifically, this treatment is given to the tooth portion of the pulley P and the lateral face of the cylindrical wall portion W.

[0053] However, the alumite treatment causes deterioration in the surface roughness of the treated surface. For this reason, there will occur aggressiveness such as increased friction coefficient relative to the drive belt V, so that reduction in the service life of the drive belt V may result to the contrary.

[0054] [Gap]

[0055] Then, in this embodiment, as shown in FIG. 1 and FIG. 3, an arrangement is provided such that operating fluid for the sake of lubrication may be fed to the drive belt V through a gap between the housing H and the front plate FP and the rear plate RP.

[0056] More particularly, between the housing H and the front plate FP and the rear plate RP, gaps G are provided which allow outflow of oil as the operating fluid. Such gaps G are formed e.g. by increasing the surface roughness of a contacting face W2, which is a surface of the housing H that comes into contact with the front plate FP or the rear plate RP, by means of the above-described alumite treatment.

[0057] The contacting face W2 of the housing H is brought into direct contact with a contacting face FP1 of the front plate FP or a contacting face RP1 of the rear plate RP each other.

[0058] With the above-described arrangement, in association with rotation of the driving rotary body A, an appropriate amount of oil will outflow through the gap and will flow to the outer side by the centrifugal force. This flowing oil will reach the pulley P disposed on the outer side of the housing H and the drive belt V wound around the pulley P, thus lubricating the pulley P and the drive belt V. Needless to say, the drive belt V used should be made of material suitable for the oil lubrication.

[0059] Further, with the alumite treatment of the contacting face W2, the surface hardness of this contacting face W2 is enhanced. Therefore, at the time of fastening with the front plate FP and the rear plate RP, even if the fastening force of the fastening bolt 5 is too strong, deformation of the cylindrical wall portion W can be prevented.

[0060] Further, with the above-described arrangement, there is no need to provide special sealing material between the cylindrical wall portion W and the front plate FP or the rear plate RP, so the configuration of the driving rotary body A can be simplified.

[0061] In this way, with the driving rotary body A having the above-described arrangement, the configuration of the driving rotary body A can be simplified and at the same time frictional wear of the pulley P and the drive belt V can be reduced. Consequently, it is possible to obtain a valve opening/closing timing control device which is highly reliable.

[0062] Incidentally, for the purpose of forming the gap G, the front plate FP or the rear plate RP may be formed of aluminum material and the contacting face FP1 of the front plate FP or the contacting face RP1 of the rear plate RP may be subjected to alumite treatment for enhancing the surface roughness of these faces.

[0063] [Groove Portion]

[0064] In the driving rotary body A used in this embodiment, between the pulley P and the cylindrical wall portion W, there are formed groove portions 9 that penetrate in the direction of the rotational axis X and extend in the circumferential direction relative to the rotational axis X. In the case of the example shown in FIG. 2, such groove portions 9 are formed over all entire regions other than those of the connecting portions 6 which connect the cylindrical wall portion W and the pulley P.

[0065] Each end portion of the groove portion 9 in the circumferential direction extends to reach a more center side of the first protruding portion 1 than the lateral face of this first protruding portion 1. Namely, a circumferential length of the respective connecting portion 6 which is the region sandwiched between two adjacent groove portions 9 is set shorter than the circumferential length of the first protruding portion 1 corresponding to the respective connecting portion 6. The reason for this is as follows. Namely, by securing a large area for the groove portion 9 relative to the region where the second protruding portion 2 of the driven rotary body B comes into sliding contacting with the inner circumferential face W1 of the cylindrical wall portion W, even if deformation should occur in the pulley P by the drive belt V, the position where such deformation is transmitted to the cylindrical wall portion W can be set away from the sliding contacting region of the second protruding portion 2.

[0066] Incidentally, the circumferential length of the groove portion 9 need not necessarily be longer than the circumferential length of the sliding contacting region of the second protruding portion 2. For, such effect of preventing transmission of deformation of the pulley P to the cylindrical wall portion W can be achieved as long as there is present, even of a very small amount, a region where the groove portion 9 and the sliding contacting region are overlapped with each other along the radial direction of the rotational axis X.

[0067] Further, with formation of such groove portions 9 above, when there occurs rise of temperature in the driving rotary body A in the course of operation of the internal combustion engine, such heat will less likely be conducted to the pulley P. Therefore, heat deterioration of the drive belt V can be prevented. First of all, the provision of the groove portions 9 can achieve reduction in the amount of aluminum material used as well as weight reduction of the driving rotary body A.

[0068] On the other hand, as for a width 9a of the groove portion 9 in the radial direction, this can vary in size in many ways. Basically, by proving the groove portion 9 to render the cylindrical wall portion W and the pulley P away from each other in the radial direction, this will make deformation in the pulley P to be transmitted less likely to the cylindrical wall portion W. However, advantageously, this width 9a of the groove portion 9 will be formed greater than a width W3 of the contacting face W2 of the housing H.

[0069] The housing H in this arrangement is formed by extrusion molding of the aluminum material. Therefore, by setting the width 9a of the groove portion 9 greater than the width W3 of the contacting face W2, it becomes possible to locate the position of the pulley P on the radially outer side from the outer face of the cylindrical wall portion W, thus forming the pulley P of a predetermined outside diameter and also to reduce the extrusion amount of the aluminum material by the amount corresponding to the groove portion 9. In this, if the width 9a of the groove portion 9 is too short, the portion corresponding to the groove portion 9 at the time of extrusion molding will become too narrow, thus making the molding difficult and causing reduction in the service life of the mold also. Then, by setting the width 9a of the groove portion 9 greater than the width W3 of the contacting face W2, the sizes of the mold will become appropriate, so that an extrusion mold that can be readily manufactured and that has good durability can be obtained. With appropriate setting of the width 9a of the groove portion 9, extrusion resistance experienced by the aluminum material in the course of extrusion molding will be reduced and the manufacture efficiency will improve.

[0070] Moreover, with the setting of the width 9a of the groove portion 9 greater than the width W3 of the contacting face W2, when e.g. the front plate FP is to be bolt-fastened to the cylindrical wall portion W, transmission of the fastening force applied to the cylindrical wall portion W to the pulley P beyond the connecting portion 6 can be prevented. Therefore, the shape of the pulley P can be maintained as a true circle, so no rotational shake will occur, and damage to the drive belt V can be prevented.

Other Embodiments

[0071] Not only the housing H, but also the front plate FP and the rear plate RP can be formed of aluminum material.

[0072] With the above-described arrangement, there is achieved significant reduction in the weight of the driving rotary body A. In such arrangement, however, the female thread portion 8 of the rear plate RP used for fixing the fastening bolt 5 should have a necessary length along the longitudinal direction of the fastening bolt 5 in order to be able to withstand sufficient fastening torque.

[0073] As the gap provided between the cylindrical wall portion W and the front plate FP or between the cylindrical wall portion W and the rear plate RP, a recess extending in the radial direction relative to the cylindrical wall portion W, the front plate FP or the rear plate RP can be provided. Such recess can be formed by cutting, molding or embossing. With the recess formed as such, it is possible to freely set the outflow position and/or outflow amount of the oil, so that more accurate lubricating effect can be achieved.

INDUSTRIAL APPLICABILITY

[0074] The present invention is widely applicable to various kinds of valve opening/closing timing control device configured to effect phase control by feeding/discharging of operating fluid.

DESCRIPTION OF REFERENCE MARKS/NUMERALS

[0075] 1: first protruding portion (partitioning portion) [0076] 2: second protruding portion (partitioning portion) [0077] 9: groove portion [0078] A: driving rotary body [0079] B: driven rotary body [0080] C: cam shaft [0081] FP: front plate [0082] FP1: contacting face of front plate [0083] RP: rear plate [0084] RP1: contacting face of rear plate [0085] H: housing [0086] P: pulley [0087] R: fluid pressure chamber [0088] R1: advance chamber [0089] R2: retard chamber [0090] V: drive belt [0091] W: cylindrical wall portion [0092] W1: inner circumferential face [0093] W2: contacting face of housing [0094] X: rotational axis [0095] Z: crank shaft