Valve opening / closing timing control device

Abstract

Provided is a valve opening / closing timing control device capable of suppressing fluctuations in a spring load even if the position of an internal spring member in a recessed portion fluctuates. A valve opening / closing timing control device is provided with a driving-side rotating body, a driven-side rotating body, and a phase adjustment mechanism. The phase adjustment mechanism is provided with: an internally toothed output gear coaxial with the rotating shaft core (X) and rotating integrally with the driven-side rotating body; an external tooth type input gear disposed on the inner side of the output gear and rotating about an eccentric shaft core (Y); and an eccentric member (26). In a recessed portion (70) of a spring member that engages an input gear and an output gear, a top surface (70af) is formed on a spring support surface (70a) that receives the biasing force of the spring member (71), and when viewed in the direction of an eccentric shaft core (Y), the top surface (70af) has a lower surface area than an eccentric arc surface (Sy) centered on the eccentric shaft core (Y), and the surface area of the top surface (70af) is greater than the surface area of the eccentric arc surface (Sy) centered on the eccentric shaft core (Y). The amount of protrusion at the central position (F) in the circumferential direction of the spring support surface (70a) is small.

Description

Technical Field

[0001] The present invention relates to a valve opening and closing timing control device. Background Art

[0002] As a valve opening and closing period control device, the valve timing device described in patent document 1 has the following structure: a concave accommodating portion (64) is formed on the eccentric outer peripheral surface (40) of the planetary carrier (32 in the document), and a spring member (70) is embedded in the accommodating portion (64) so ​​that the elastic force of the spring member (70) is applied to the planetary gear (33).

[0003] In addition, in the structure of Patent Document 1, the elastic force of the spring member (70) applies the external gear portion (39) of the planetary gear (33) to the internal gear portion (31) along the action line (L), but the action line (L) is inclined relative to the eccentric direction line (E).

[0004] Patent Document 1: Japanese Patent Application Laid-Open No. 2008-38886

[0005] As described in Patent Document 1, in a concave housing portion, the central portion of the support surface (the surface located on the rotational centerline (O) side) with which the spring member abuts is gently convex outward, and the support surface of the spring member is formed into a gently curved shape to follow this convex shape. Furthermore, the concave housing portion has wall-like portions formed at both circumferential ends to restrict the circumferential movement of the spring member with respect to the planetary carrier.

[0006] The valve timing control device rotates at high speed. Due to the correlation between spring load and vibration, it is desired that load fluctuation be small even when the position of the spring member in the concave housing fluctuates.

[0007] On the other hand, even if a wall portion is formed at the circumferential end of the planetary carrier in the housing portion as in Patent Document 1, the positional variation of the spring member cannot be sufficiently restricted, and thus the spring member may still be displaced.

[0008] When the spring member is displaced in this manner, the positional relationship between the protrusion on the support surface of the housing portion and the spring member in contact therewith changes, causing a change in the load on the spring member. As a result, vibration may increase. Summary of the Invention

[0009] For these reasons, there is a demand for a valve opening / closing timing control device that can suppress fluctuations in the spring load even when the position of the internal spring member in the concave portion fluctuates.

[0010] The valve timing control device of the present invention is characterized by comprising: a driving-side rotor that rotates synchronously with the crankshaft of an internal combustion engine about a rotation axis; a driven-side rotor that is coaxially arranged inside the driving-side rotor and rotates integrally with the camshaft for valve opening and closing of the internal combustion engine; and a phase adjustment mechanism that adjusts the relative rotational phase between the driving-side rotor and the driven-side rotor. The phase adjustment mechanism comprises: an internally toothed output gear that is coaxially arranged with the rotation axis and rotates integrally with the driven-side rotor; an externally toothed input gear that has fewer teeth than the output gear and is arranged inside the output gear and rotates about an eccentric axis parallel to the rotation axis; a joint member that interlocks the input gear with the rotation of the driving-side rotor; an eccentric member that meshes the external teeth of the input gear with the internal teeth of the output gear; and an electric actuator that drives the eccentric member to rotate about the rotation axis. The eccentric member is formed with a concave portion that is recessed radially inward from an outer surface of the eccentric member to accommodate a spring component that applies a force that causes the external tooth portion of the input gear to mesh with the internal tooth portion of the output gear. In the concave portion, a top surface is formed on a spring support surface that receives the force of the spring component. When viewed in the direction of the eccentric shaft core, the top surface protrudes less at a central position in the circumferential direction of the spring support surface than an eccentric circular arc surface centered on the eccentric shaft core.

[0011] According to this characteristic configuration, the spring member embedded in the recessed portion applies a force from the spring support surface of the recessed portion toward the inner circumference of the input gear, maintaining a state in which the external teeth of the input gear and the internal teeth of the output gear mesh. Furthermore, within the recessed portion, the spring support surface that bears the spring member's force is formed with an arc-shaped top surface having a large radius of curvature. When viewed along the eccentric shaft core, this top surface protrudes less from the circumferential center of the spring support surface than the eccentric arc surface centered on the eccentric shaft core. Therefore, even if the spring member is circumferentially displaced within the recessed portion, fluctuations in the force are suppressed. Consequently, a valve timing control device is provided that suppresses fluctuations in the spring load even if the position of the spring member within the recessed portion fluctuates. BRIEF DESCRIPTION OF THE DRAWINGS

[0012] Figure 1 It is a cross-sectional view of the valve opening and closing timing control device.

[0013] Figure 2 yes Figure 1 Cross-sectional view along line II-II.

[0014] Figure 3 yes Figure 1Cross-sectional view along line III-III.

[0015] Figure 4 yes Figure 1 Sectional view along line IV-IV.

[0016] Figure 5 This is an exploded perspective view of the valve opening and closing timing control device.

[0017] Figure 6 This is an enlarged view showing the positional relationship among the concave portion, the spring material, the output gear, and the input gear.

[0018] Figure 7 It is a perspective view of a pair of spring members.

[0019] Figure 8 It is a cross-sectional view showing the shape of the spring support surface.

[0020] Figure 9 It is a perspective view of the eccentric member showing the position of the rough surface.

[0021] Description of Reference Numerals

[0022] 1: Crankshaft, 2: Intake camshaft (camshaft), 25: Output gear, 26: Eccentric member, 26E: Eccentric support surface, 26d: Annular groove, 30: Input gear, 31: Fixed ring, 40: Joint member, 70: Concave portion, 70a: Spring support surface, 70af: Top surface, 71: Spring member, 100: Valve opening and closing timing control device, A: Driving side rotor, B: Driven side rotor, C: Phase adjustment mechanism, E: Internal combustion engine (engine), F: Center position, M: Phase control motor (electric actuator), RF: Rough surface, Sy: Eccentric arc surface, Tc: Center thickness, Te: End thickness, X: Rotating axis core, Y: Eccentric axis core DETAILED DESCRIPTION

[0023] Hereinafter, embodiments of the valve opening and closing timing control device of the present invention will be described with reference to the drawings. However, the present invention is not limited to the following embodiments, and various modifications are possible without departing from the spirit and scope of the present invention.

[0024] Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

[0025] [Basic composition]

[0026] like Figure 1As shown, the valve opening and closing timing control device 100 of this embodiment includes: a driving side rotating body A, which rotates synchronously with the crankshaft 1 of the engine E as an internal combustion engine; a driven side rotating body B, which rotates integrally with the intake camshaft 2 that opens and closes the intake valve 2B (an example of a valve); and a phase adjustment mechanism C, which uses the driving force of the phase control motor M to set the relative rotational phase between the driving side rotating body A and the driven side rotating body B.

[0027] The driving-side rotor A and the driven-side rotor B included in the valve opening / closing timing control device 100 are relatively rotatable within a set range around a rotation axis X.

[0028] The engine E is a four-stroke engine in which pistons 4 are housed in a plurality of cylinders 3 formed in a cylinder block, and these pistons 4 are connected to a crankshaft 1 via connecting rods 5. A timing chain 6 (which may also be a timing belt, etc.) is wound around an output sprocket 1S of the crankshaft 1 of the engine E and a drive sprocket 11S of the drive-side rotating body A.

[0029] Thus, when the engine E is operating, the valve opening and closing timing control device 100 as a whole rotates about the rotation axis X. The phase adjustment mechanism C uses the driving force of the phase control motor M to set the relative rotational phase between the driving-side rotor A and the driven-side rotor B, thereby controlling the opening and closing timing (opening and closing timing) of the intake valve 2B driven by the cam portion 2A of the intake camshaft 2.

[0030] [Valve opening and closing timing control device]

[0031] like Figure 1 As shown, the driving side rotating body A fastens an outer housing 11 having a driving sprocket 11S formed on its outer periphery and a front plate 12 with a plurality of fastening bolts 13. The outer housing 11 is a bottomed cylindrical type having an opening at the bottom.

[0032] like Figures 1 to 5 As shown, the internal space of the outer shell 11 accommodates the intermediate member 20 as the driven side rotating body B and the phase adjustment mechanism C having a gear reduction mechanism (see Figure 3 The phase adjustment mechanism C has an Oldham joint Cx (see Figure 4 、 Figure 5 ).

[0033] The intermediate member 20 is integrally formed by a supporting wall portion 21 and a cylindrical wall portion 22, wherein the supporting wall portion 21 is connected to the intake camshaft 2 in a posture perpendicular to the rotating axis core X, and the cylindrical wall portion 22 is cylindrical with the rotating axis core X as the center and protrudes in the direction away from the intake camshaft 2.

[0034] The intermediate member 20 is rotatably fitted into the outer housing 11 with the outer surface of the cylindrical wall portion 22 in contact with the inner surface of the outer housing 11 , and is fixed to the end of the intake camshaft 2 by a fastening bolt 23 inserted through a central through-hole of the support wall portion 21 .

[0035] like Figure 1 、 Figure 5 As shown, a groove portion 22 a for retaining lubricating oil is formed on the outer peripheral side of the cylindrical wall portion 22 over the entire circumference.

[0036] like Figure 1 As shown, the phase control motor M is supported by the support frame 7 on the engine E in such a manner that its output shaft Ma is arranged on the same axis as the rotation axis X. A pair of engagement pins 8 (also see FIG. 1 ) are formed on the output shaft Ma of the phase control motor M in a manner perpendicular to the rotation axis X. Figure 4 ).

[0037] Phase adjustment mechanism

[0038] like Figure 1 、 Figure 5 As shown, the phase adjustment mechanism C includes an intermediate member 20, an output gear 25 formed on the inner circumferential surface of the cylindrical wall portion 22 of the intermediate member 20, an eccentric member 26, a biasing mechanism S, a first bearing 28, a second bearing 29, an input gear 30, a retaining ring 31, an annular spacer 32, and an Oldham joint Cx. While rolling bearings are used for the first bearing 28 and the second bearing 29, sliding bearings may also be used.

[0039] like Figure 1 As shown, in the inner circumference of the cylindrical wall portion 22 of the intermediate component 20, in the direction along the rotating axis core X (hereinafter referred to as the axial direction), a support surface 22S centered on the rotating axis core X is formed on the inner side (adjacent to the support wall portion 21), and an output gear 25 centered on the rotating axis core X is integrally formed on the outer side (the side farther from the intake camshaft 2) than the support surface 22S.

[0040] like Figure 1 、 Figure 2 and Figure 5 As shown in FIG. 1 , the eccentric member 26 is cylindrical. The eccentric member 26 has a circumferential support surface 26S formed on the inner side in the axial direction (the side closer to the intake camshaft 2) of the outer peripheral surface centered on the rotation axis X. Figure 1 、 Figure 3 and Figure 5 As shown, the eccentric member 26 has an eccentric support surface 26E formed on the outer side (the side farther from the intake camshaft 2) of the outer peripheral surface centered on an eccentric shaft core Y that is eccentric and parallel to the rotation axis X. Since the direction along the eccentric shaft core Y is the same as the axial direction, the direction along the eccentric shaft core Y will be simply referred to as the axial direction hereinafter.

[0041] like Figure 5 、 Figure 6 As shown, a concave portion 70 is formed on the eccentric support surface 26E. The concave portion 70 is recessed radially inward of the eccentric member 26 and is open in the axial direction toward the end (outer end direction: toward the front plate 12). The concave portion 70 has a spring support surface 70a and end wall surfaces 70b at both ends in the circumferential direction.

[0042] like Figure 6 、 Figure 8 As shown, the spring support surface 70a is formed into a shape in which the central portion in the circumferential direction is displaced radially inward compared to the arc surface centered on the eccentric shaft core Y (the details of this structure will be described later). Figure 6 、 Figure 8 、 Figure 9 As shown, the pair of end wall surfaces 70b are flat when viewed in the direction of the eccentric shaft core Y, and are formed symmetrically in the circumferential direction.

[0043] As will be described later, a pair of spring members 71 constituting the urging mechanism S is fitted into the concave portion 70 .

[0044] like Figure 1 、 Figure 5 As shown, a pair of engagement grooves 26T are formed on the inner periphery of the eccentric member 26 in a posture parallel to the rotating shaft core X. The pair of engagement grooves 26T can respectively engage with the phase control motor M (see Figure 1 ) is engaged with a pair of engaging pins 8.

[0045] like Figure 1 、 Figure 2 、 Figure 3 、 Figure 6 As shown, by fitting the first bearing 28 onto the circumferential support surface 26S and embedding the first bearing 28 into the support surface 22S of the cylindrical wall portion 22, the eccentric member 26 is rotatably supported on the intermediate member 20 about the rotation axis X. Figure 1 、 Figure 3 As shown, the input gear 30 is rotatably supported on the eccentric support surface 26E of the eccentric member 26 through the second bearing 29 about the eccentric shaft core Y.

[0046] In this phase adjustment mechanism C, the number of teeth of the external teeth portion 30A of the input gear 30 is one less than the number of teeth of the internal teeth portion 25A of the output gear 25 , and a portion of the external teeth portion 30A of the input gear 30 meshes with a portion of the internal teeth portion 25A of the output gear 25 .

[0047] An urging mechanism S, including a pair of spring members 71, applies an urging force to the input gear 30 via the second bearing 29, causing a portion of the external teeth 30A of the input gear 30 to mesh with a portion of the internal teeth 25A of the output gear 25. Furthermore, by fitting the inner race 29a of the second bearing 29 onto the eccentric support surface 26E of the eccentric member 26 and fitting the outer race 29b of the second bearing 29 onto the inner circumference of the input gear 30, the urging force of the urging mechanism S is applied radially to the input gear 30.

[0048] like Figure 7 As shown, the urging mechanism S is constructed by combining a pair of spring members 71 of the same shape and size.

[0049] like Figure 6 、 Figure 7 As shown, the spring member 71 is integrally formed by a bent portion 72 that bends the spring plate, a support portion 73 that extends from one side of the spring plate of the bent portion 72 and faces the spring support surface 70a of the concave portion 70, and a biasing portion 74 that extends from the other side of the spring plate of the bent portion 72 and applies a force to the inner circumferential side of the input gear 30, and a bent portion 75 is provided on the top end side of the support portion 73 that is bent into a posture separated from the spring support surface 70a of the concave portion 70.

[0050] That is, the bent portion 72 is formed by bending the spring plate material so that it becomes a U-shape when viewed along the eccentric axis Y when fitted into the concave portion 70 , thereby forming a shape in which the support portion 73 and the biasing portion 74 are arranged in a substantially parallel posture.

[0051] Therefore, if Figure 7 As shown, a support-side cutout 73 a is formed at the boundary between the curved portion 72 and the support portion 73 , and a force-applying-side cutout 74 a is formed at the boundary between the curved portion 72 and the force-applying portion 74 .

[0052] exist Figure 6 、 Figure 7 In the illustrated direction, the two spring members 71 form a biasing mechanism S arranged in mutually opposite positions so that the respective curved portions 72 are arranged at the circumferential ends of the concave portion 70 and are embedded in one concave portion 70. By being embedded in this way, the curved portions 72 of the two spring members 71 are separated, and the two biasing portions 74 are arranged side by side in the axial direction.

[0053] The spring member 71 is bent along the spring support surface 70a of the concave portion 70 in the area from the bent portion 72 to the support portion 73, and forms a base end side abutment portion Q at a position facing the spring support surface 70a in the bent portion 72, and forms a top end side abutment portion R at the boundary between the support portion 73 and the bent portion 75.

[0054] Furthermore, if Figure 6 As shown, the force-applying portion 74 causes the force-applying top portion 74b to protrude radially outward of the eccentric member 26 so that the force is concentratedly applied in the direction where the outer tooth portion 30A of the input gear 30 and the inner tooth portion 25A of the output gear 25 in the inner surface of the inner ring 29a of the second bearing 29 are most deeply engaged.

[0055] The bent portion 72 is the main part that generates the force of the spring member 71 by elastic deformation. By combining the two spring members 71 and inserting them into the concave portion 70, as shown in FIG. Figure 6 、 Figure 7 As shown, the force application tops 74b of the force application portions 74 of the two spring members 71 are arranged at overlapping positions when viewed along the eccentric axis Y. In this manner, although the two spring members 71 are embedded in one concave portion 70, the forces applied to the input gear 30 can be balanced.

[0056] Thus, while the two spring members 71 are in contact with the spring support surface 70a of the concave portion 70 using the base-side contact portion Q at the boundary between the support portion 73 and the curved portion 72 as a fulcrum, the biasing force from the biasing top portions 74b of the two biasing portions 74 can be applied to the inner race 29a of the second bearing 29. Furthermore, while the biasing force is applied in this manner, the distal-side contact portion R at the boundary between the curved portion 75 and the support portion 73 is maintained in contact with the spring support surface 70a of the concave portion 70.

[0057] 〔Retaining ring / spring member〕

[0058] like Figure 1 、 Figure 5 、 Figure 9 As shown, the fixing ring 31 is fitted into the annular groove 26d formed in an annular shape on the outer periphery of the eccentric support surface 26E of the eccentric member 26. The valve timing control device 100 includes a spacer 32 at a position contacting the fixing ring 31 to prevent the second bearing 29 from coming off.

[0059] [Phase adjustment mechanism: Cross slide joint]

[0060] like Figure 1 、 Figure 4 、 Figure 5 As shown, the cross slider joint Cx is composed of a plate-shaped joint member 40, which is integrally formed with a central annular portion 41, a first direction (in the Figure 4 A pair of outer engaging arms 42 projecting radially outward from the annular portion 41, and a pair of outer engaging arms 42 projecting radially outward from the annular portion 41 in a direction perpendicular to the first direction ( Figure 4The inner engaging arms 43 protrude radially outward from the annular portion 41 in the vertical direction. The pair of inner engaging arms 43 are respectively formed with engaging recesses 43a connected to the openings of the annular portion 41.

[0061] A pair of guide grooves 11a are formed in the opening edge of the outer shell 11, which abuts the front plate 12, extending radially from the interior of the outer shell 11 to the exterior. The width of these guide grooves 11a is set slightly wider than the width of the external engagement arm 42, and a pair of discharge passages 11b are formed in each guide groove 11a. Alternatively, the discharge passages 11b can be configured to allow lubricating oil to flow radially relative to the front plate 12.

[0062] The outer housing 11 has a pocket 11c formed at the opening edge, outside the guide groove 11a, by cutting out the inner circumference in the circumferential direction. Foreign matter that is moved outward by the centrifugal force of the driving rotor A is collected in the pocket 11c.

[0063] The input gear 30 has a pair of engaging protrusions 30T integrally formed on the end surface facing the front plate 12. The engaging width of the engaging protrusions 30T is set slightly narrower than the engaging width of the engaging recess 43a of the inner engaging arm 43.

[0064] Thus, the pair of external engaging arms 42 of the joint member 40 engage with the pair of guide grooves 11a of the outer housing 11, and the pair of engaging protrusions 30T of the input gear 30 engage with the engaging recesses 43a of the pair of internal engaging arms 43 of the joint member 40, thereby enabling the Oldham joint Cx to function.

[0065] In addition, the joint member 40 can be arranged relative to the outer housing 11 in the first direction ( Figure 4 The input gear 30 is displaced in the second direction (in the left and right direction) relative to the joint member 40 along the formation direction of the engagement recess 43a of the internal engagement arm 43. Figure 4 The middle direction is up and down) and the upper position can be moved freely.

[0066] [Lubrication of phase adjustment mechanism]

[0067] like Figure 1 As shown, a lubricating oil passage 15 is formed in the intake camshaft 2 to supply lubricating oil from an external oil pump P via an oil passage forming member 9. The support wall portion 21 of the intermediate member 20 has an opening 21a formed inside the eccentric member 26 for guiding oil relative to a portion of the surface that contacts the intake camshaft 2.

[0068] Lubricating oil is supplied to the eccentric member 26 through the opening 21a. Furthermore, a lubricating recess 12a is formed radially on the surface of the front plate 12 that faces the joint member 40, creating a small gap between the surface of the joint member 40 and the front plate 12. Lubricating oil is also supplied to this lubricating recess 12a. While this lubricating recess 12a is formed on the inner circumference of the front plate 12, it can also be formed in an area that reaches the outer circumference of the front plate 12. Alternatively, the lubricating recess 12a can be omitted so that lubricating oil is supplied to the gap between the front plate 12 and the joint member 40.

[0069] As described above, a pair of discharge flow paths 11b are formed in the guide groove portion 11a (see Figure 4 、 Figure 5 Furthermore, by making the opening diameter of the opening 12 b of the front plate 12 sufficiently larger than the inner diameter of the eccentric member 26 , a difference in opening diameter is set between the opening edge of the front plate 12 and the inner periphery of the eccentric member 26 .

[0070] With this configuration, lubricating oil supplied from the oil pump P is supplied from the lubricating oil passage 15 of the intake camshaft 2 to the interior space of the eccentric member 26 via the opening 21a of the support wall portion 21 of the intermediate member 20. The lubricating oil thus supplied is supplied from the eccentric member 26 to the first bearing 28 by centrifugal force, thereby enabling smooth operation of the first bearing 28.

[0071] At the same time, the lubricating oil in the interior space of the eccentric member 26 is supplied to the joint member 40 by centrifugal force, supplied to the second bearing 29 , and supplied between the internal teeth 25A of the output gear 25 and the external teeth 30A of the input gear 30 .

[0072] In addition, if Figure 1 As shown, the lubricating oil from the second bearing 29 is supplied between the front plate 12 and the joint member 40 through the lubricating recess 12a, and is supplied to the gap between the outer engaging arm 42 of the joint member 40 and the guide groove portion 11a of the outer shell 11 (see also Figure 5 The lubricating oil supplied to the joint member 40 is discharged to the outside from the gap between the external engagement arm 42 of the joint member 40 and the guide groove portion 11 a of the outer housing 11 .

[0073] like Figure 5 As shown, a protrusion 12c protruding inward is formed on the inner surface of the front plate 12 (the side closest to the intake camshaft 2). The protrusion 12c gently abuts the intermediate member 20, allowing for sliding contact. This abutment with the protrusion 12c restricts movement of the intermediate member 20 toward the front plate 12. This allows the Oldham joint Cx (joint member 40) to operate smoothly while maintaining a predetermined gap between the front plate 12 and the intermediate member 20.

[0074] [Operation of the phase adjustment mechanism]

[0075] Although not shown in the drawings, the phase control motor M is controlled by a control device configured as an ECU. The control device includes sensors in the engine E that can detect the rotational speed (rotational speed per unit time) and rotational phase of the crankshaft 1 and intake camshaft 2. Detection signals from these sensors are input to the control device.

[0076] The control device maintains the relative rotational phase by driving the phase control motor M at a speed equal to the rotational speed of the intake camshaft 2 while the engine E is running. To achieve this, the phase control motor M is driven at a speed lower than the rotational speed of the intake camshaft 2 to advance the angle of rotation. Conversely, the phase control motor M is driven at a speed higher to retard the angle of rotation.

[0077] When the phase control motor M rotates at the same speed as the outer housing 11 (the same speed as the intake camshaft 2), the meshing position of the outer tooth portion 30A of the input gear 30 and the inner tooth portion 25A of the output gear 25 remains unchanged, so the relative rotational phase of the driven side rotating body B with respect to the driving side rotating body A is maintained.

[0078] In contrast, by driving the output shaft Ma of the rotary phase control motor M at a higher or lower speed than the rotational speed of the outer housing 11, the eccentric shaft core Y revolves about the rotational shaft core X in the phase adjustment mechanism C. Due to this revolution, the meshing position of the external teeth 30A of the input gear 30 with the internal teeth 25A of the output gear 25 is displaced along the inner circumference of the output gear 25, and a rotational force is applied between the input gear 30 and the output gear 25. In other words, a rotational force centered on the rotational shaft core X is applied to the output gear 25, while a rotational force caused by the rotation centered on the eccentric shaft core Y is applied to the input gear 30.

[0079] As described above, the engagement protrusion 30T of the input gear 30 engages with the engagement recess 43a of the internal engagement arm 43 of the joint member 40, preventing rotation relative to the outer housing 11. A rotational force is applied to the output gear 25. This application of rotational force causes the intermediate member 20 and the output gear 25 to rotate together relative to the outer housing 11 about the rotation axis X. As a result, the relative rotational phase between the driving-side rotor A and the driven-side rotor B is set, enabling the intake camshaft 2 to set the opening and closing timing.

[0080] In addition, when the eccentric shaft core Y of the input gear 30 revolves around the rotating shaft core X, as the input gear 30 is displaced, the joint member 40 of the cross slider joint Cx is displaced relative to the outer shell 11 in the direction (first direction) in which the external locking arm 42 extends, and the input gear 30 is displaced in the direction (second direction) in which the internal locking arm 43 extends.

[0081] As described above, the number of teeth of the external tooth portion 30A of the input gear 30 is set to be one tooth less than the number of teeth of the internal tooth portion 25A of the output gear 25. Therefore, when the eccentric shaft core Y of the input gear 30 completes one revolution around the rotating shaft core X, the output gear 25 only rotates by one tooth, achieving a large deceleration.

[0082] [Concave part]

[0083] like Figure 6 、 Figure 8 As shown, the concave portion 70 is a shape that is recessed radially inward from the eccentric support surface 26E (an example of an eccentric outer surface) when viewed along the direction of the eccentric shaft core Y. In addition, when viewed along the direction of the eccentric shaft core Y, the end of the spring support surface 70a in the circumferential direction of the eccentric member 26 and the end wall surfaces 70b at both ends are formed so as to smoothly connect with each other via curved surfaces 70c.

[0084] When the two spring members 71 are fitted into the concave portion 70 , their respective base end abutting portions Q abut against the end wall surface 70 b and the spring support surface 70 a , and their respective distal end abutting portions R abut against the spring support surface 70 a .

[0085] The spring support surface 70a of the concave portion 70 is formed by a bulging surface St having a larger curvature radius than the eccentric arc surface Sy having an eccentric side radius Ry with the eccentric shaft core Y as the center, so as to reduce the circumferential center position F of the spring support surface 70a (at Figure 8 The area near the center position F in the bulging surface St is called the top surface 70af.

[0086] The bulging surface St is formed as an arc with a center radius Rx centered on the rotation axis X. The bulging surface St is not limited to an arc surface, and may be, for example, a portion of an elliptical curve or a portion of a quadratic function curve.

[0087] In this configuration, the circumferential center position F of the eccentric arc surface Sy in the middle concave portion 70 and the circumferential center position F of the top surface 70 af in the concave portion 70 are separated by a gap G in the radial direction.

[0088] The eccentric member 26 is cylindrical with a cylindrical internal space centered on the eccentric shaft core Y. The radial thickness from the inner peripheral surface of the eccentric member 26 to the central position F of the spring support surface 70a, i.e., the central thickness Tc, is set to be smaller than the thickness from the inner peripheral surface of the eccentric member 26 to the two end portions in the circumferential direction of the spring support surface 70a, i.e., the end thickness Te.

[0089] Furthermore, the top surface 70af of the spring support surface 70a is formed with a rough surface RF by forming a plurality of groove-shaped portions 70d along the eccentric axis Y. The plurality of groove-shaped portions 70d are formed by a laser beam, and by forming the rough surface RF in this way, the spring member 71 is prevented from moving in the circumferential direction relative to the spring support surface 70a (see also FIG. Figure 9 ).

[0090] In this configuration, the two spring members 71 embedded in the recessed portion 70 apply a force from the spring support surface 70 a of the recessed portion 70 toward the inner circumference of the input gear 30 , thereby maintaining the meshing state between the external teeth 30A of the input gear 30 and the internal teeth 25A of the output gear 25 .

[0091] In this configuration, when viewed along the eccentric axis Y, the top surface 70 af of the spring support surface 70 a is formed to project less at the center position F in the circumferential direction than at the eccentric arc surface Sy. Therefore, even if the spring member 71 is displaced away from the center position F within the recessed portion 70 , the change in the acting force is minimized, preventing vibration from occurring during high-speed rotation of the valve opening and closing timing control device 100 .

[0092] In addition, since the top side abutment portion R of the spring component 71 of this embodiment is in contact with the vicinity of the circumferential center position F of the spring support surface 70a, when the spring component 71 is displaced in the direction away from the center position F inside the concave portion 70, the top side abutment portion R moves in contact with the top surface 70af. Even with such movement, the change in the force applied from the spring component 71 can be suppressed.

[0093] In this configuration, the rough surface RF is formed on the spring support surface 70 a . Therefore, as described above, when the spring member 71 moves in the circumferential direction of the spring support surface 70 a , frictional force acts on the distal end contact portion R, thereby suppressing movement of the spring member 71 .

[0094] [Other Implementation Methods]

[0095] In addition to the above-described embodiment, the present invention may also be configured as follows (the same numerals and reference signs are given to embodiments having the same functions as those of the embodiment).

[0096] (a) As described in part of the embodiment, the bulging surface St is not limited to an arc surface, but may also be a shape along a portion of a curve forming an ellipse, a portion of a curve forming a quadratic function, or a curve connecting multiple functions in a gently convex manner.

[0097] (b) The spring member 71 may be a single member.

[0098] (c) For example, the rough surface RF may be formed by knurling. Alternatively, the spring support surface 70a may be formed into the rough surface RF using a surface processing machine.

[0099] In addition, the configuration disclosed in the above-mentioned embodiment (including other embodiments, the same below) can be combined with the configuration disclosed in other embodiments as long as no contradiction occurs. In addition, the embodiments disclosed in this specification are examples, and the embodiments of the present invention are not limited to this and can be appropriately changed within the scope of the purpose of the present invention.

[0100] In the above-mentioned embodiment, the following configuration is conceived.

[0101] (1) A valve opening and closing timing control device 100, wherein:

[0102] It comprises: a driving side rotating body A, which rotates synchronously with the crankshaft 1 of the internal combustion engine (engine E) with the rotating shaft core X as the center; a driven side rotating body B, which is arranged on the inner side of the driving side rotating body A coaxially with the rotating shaft core X, and rotates integrally with the camshaft (intake camshaft 2) for opening and closing the valves of the internal combustion engine (engine E); and a phase adjustment mechanism C, which adjusts the relative rotational phase of the driving side rotating body A and the driven side rotating body B. The phase adjustment mechanism C includes: an internally toothed output gear 25, which is coaxial with the rotating shaft core X and rotates integrally with the driven-side rotating body B; an externally toothed input gear 30, which is arranged on the inner side of the output gear 25 with a smaller number of teeth than the output gear 25 and rotates around an eccentric shaft core Y in a posture parallel to the rotating shaft core X; a joint member 40, which links the rotation of the input gear 30 with that of the driving-side rotating body A; an eccentric member 26, which meshes the external tooth portion 30A of the input gear 30 with the internal tooth portion 25A of the output gear 25; and an electric actuator (phase control motor M) which drives the eccentric member 26 to rotate around the rotating shaft core X. A concave portion 70 is formed in the eccentric member 26, which is recessed radially inward from the outer surface of the eccentric member 26, to accommodate a spring component 71. The spring component 71 applies a force that causes the external tooth portion 30A of the input gear 30 to mesh with the internal tooth portion 25A of the output gear 25. In the concave portion 70, a top surface 70af is formed on a spring support surface 70a that receives the force of the spring component 70. When viewed in the direction of the eccentric shaft core Y, the top surface 70af protrudes less at a circumferential center position F in the spring support surface 70a than the eccentric circular arc surface Sy centered on the eccentric shaft core Y.

[0103] As a result, the spring member 71 embedded in the recessed portion 70 applies a force from the spring support surface 70a of the recessed portion 70 toward the inner circumference of the input gear 30, maintaining the meshing state between the external teeth 30A of the input gear 30 and the internal teeth 25A of the output gear 25. Furthermore, the recessed portion 70 includes a top surface 70af formed on the spring support surface 70a. When viewed along the eccentric axis Y, this top surface 70af protrudes less from the eccentric circular arc surface Sy centered on the eccentric axis Y at the circumferential center F of the spring support surface 70a. Therefore, even if the spring member 71 displaces circumferentially within the recessed portion 70, significant fluctuations in the force applied by the spring member 71 in the direction of meshing between the external teeth 30A of the input gear 30 and the internal teeth 25A of the output gear 25 can be suppressed. Consequently, even when the valve timing control device 100 rotates at high speeds, vibrations can be suppressed.

[0104] (2) In the valve opening and closing timing control device 100 of (1), preferably, the eccentric member 26 is cylindrical having a cylindrical internal space centered on the eccentric shaft core Y, and the radial thickness from the inner peripheral surface of the eccentric member 26 to the top surface 70af in the spring support surface 70a, that is, the center thickness Tc, is set to be smaller than the thickness from the inner peripheral surface of the eccentric member 26 to the two end portions in the circumferential direction of the spring support surface 70a, that is, the end thickness Te.

[0105] Thus, the concave portion 70 is formed to be recessed relative to the eccentric member 26. Even when a load is applied to the circumferential end of the spring support surface 70a, the end side of the concave portion 70 has a higher strength in the circumferential direction, so that the end of the spring support surface 70a will not be damaged.

[0106] (3) In the valve timing control device 100 of (1) or (2), preferably, the two spring members 71 are arranged spaced apart in the circumferential direction of the concave portion 70 .

[0107] Thus, by using two spring members 71 , even if one of the spring members 71 is damaged, the meshing state of the external teeth portion 30A of the input gear 30 and the internal teeth portion 25A of the output gear 25 can be maintained.

[0108] (4) In the valve timing control device 100 according to any one of (1) to (3), preferably, the top surface 70 af of the concave portion 70 is formed as a rough surface RF.

[0109] Thus, even when an external force is applied to the spring member 71 causing it to be displaced in the circumferential direction within the concave portion 70 , the rough surface RF suppresses movement of the spring member 71 .

[0110] Industrial applicability

[0111] The present invention can be utilized in a valve opening and closing timing control device.

Claims

1. A valve opening and closing timing control device, wherein: have: The driving side rotating body rotates synchronously with the crankshaft of the internal combustion engine around the rotating shaft core. a driven-side rotating body, which is coaxially arranged inside the driving-side rotating body with the rotating shaft core and rotates integrally with a camshaft for opening and closing valves of the internal combustion engine; and a phase adjustment mechanism for adjusting the relative rotation phase between the driving-side rotating body and the driven-side rotating body; The phase adjustment mechanism comprises: The internally toothed output gear is coaxial with the rotating shaft and rotates integrally with the driven-side rotating body. The externally toothed input gear is arranged inside the output gear with a smaller number of teeth than the output gear, and rotates around an eccentric shaft parallel to the rotation shaft. A joint member that allows the input gear to rotate in conjunction with the driving side rotating body. an eccentric member that meshes the external teeth of the input gear with the internal teeth of the output gear, and an electric actuator for driving the eccentric member to rotate about the rotating shaft core; The eccentric member is formed with a concave portion recessed radially inward from an outer surface of the eccentric member to accommodate a spring member that applies a force that causes the external teeth of the input gear to mesh with the internal teeth of the output gear. In the concave portion, a top surface is formed on the spring support surface that bears the force of the spring member. When viewed in the direction of the eccentric shaft core, the top surface protrudes less at the central position in the circumferential direction of the spring support surface than the eccentric circular arc surface centered on the eccentric shaft core.

2. The valve opening and closing timing control device according to claim 1, wherein: The eccentric member is in the shape of a tube having a cylindrical inner space centered on the eccentric shaft core. The radial thickness from the inner peripheral surface of the eccentric member to the top surface of the spring support surface, i.e., the center thickness, is set smaller than the thickness from the inner peripheral surface of the eccentric member to both circumferential ends of the spring support surface, i.e., the end thickness.

3. The valve opening and closing timing control device according to claim 1 or 2, wherein: The pair of spring members are arranged spaced apart in the circumferential direction of the concave portion.

4. The valve opening and closing timing control device according to claim 1 or 2, wherein: The top surface of the concave portion is formed as a rough surface.

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