JP2008215314A - Valve timing adjusting device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve timing adjusting device improving productivity and inhibiting drop of durability and generation of abnormal noise. <P>SOLUTION: A device is provided with an electric motor including a rotary shaft body 7 provided with a pair of connecting projection part 76 projecting in a radial direction opposite side and generating controlled torque of output from the rotary shaft body 7, and a phase adjusting mechanism including a planetary carrier 40 provided with a pair of connecting structures 90 connected to each connecting projection part 76 and rotating a one unit with the rotary shaft body 7 and adjusting relative phase between a crankshaft and a camshaft according to controlled torque of input to the planetary carrier 40 from the rotary shaft body 7. Each connecting structure 90 includes a pair of fitting parts 94 formed harder than a tubular main body member 80 of the rotary shaft body 7 and fixed in an inner circumference side of the main body member 80 to be in roughly parallel with a radial direction of the main body member 80. Each connecting projection part 76 is connected to the rotary shaft body 7 by being fitted between the pair of the fitting part 94 of the corresponding connecting structure 90. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a valve timing adjusting device that adjusts the valve timing of at least one of an intake valve and an exhaust valve whose camshaft opens and closes by torque transmission from a crankshaft in an internal combustion engine.

  Conventionally, control torque is generated by torque generating means such as an electric motor or an electric brake, and the relative phase between the crankshaft and the camshaft that determines the valve timing (hereinafter referred to as “engine phase”) is adjusted according to the control torque. A valve timing adjusting device is known. As this type of valve timing adjusting device, the output rotating body of the torque generating means and the input rotating body of the phase adjusting mechanism are connected, and the phase adjusting mechanism is used in accordance with the control torque input from the output rotating body to the input rotating body. Patent Document 1 discloses an engine phase adjusted.

Now, in the valve timing adjusting device disclosed in Patent Document 1, a pair of connection protrusions that are open on the inner peripheral side of the input rotator are provided with a pair of connection protrusions that protrude on the opposite side in the radial direction of the output rotator. Respectively. This facilitates the connection work between the input rotator and the output rotator at the time of assembly, thereby improving productivity.
JP 2004-003419 A

  Now, in the valve timing adjusting device disclosed in Patent Document 1, in order to make it easy to fit each connection protrusion into each connection recess during assembly, it is necessary to secure a fitting clearance between the connection protrusion and the connection recess. It becomes important. However, when ensuring such a fitting clearance, during operation after assembling, each connection projection and each connection recess slide relative to each other due to axial misalignment or inclination between the input rotation body and the output rotation body. As a result, a large contact pressure is generated, and depending on the material, the wear proceeds. Such progress of wear may reduce the durability or increase the fitting clearance more than necessary, leading to the generation of abnormal noise. Therefore, improvement is desired.

  In order to suppress wear, a method of increasing the hardness of the entire input rotator by forming the input rotator provided with the connecting recesses with metal and performing a heat treatment can be considered. However, in this method, distortion due to heat treatment is likely to occur in the input rotator, which is not preferable particularly when dimensional accuracy is required for the input rotator.

  The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a valve timing adjusting device that enhances productivity and suppresses deterioration of durability and generation of abnormal noise. .

  The invention according to claim 1 is a valve timing adjusting device for adjusting the valve timing of at least one of an intake valve and an exhaust valve whose camshaft opens and closes by torque transmission from a crankshaft in an internal combustion engine, A torque generating means for generating a control torque output from the output rotator, and a pair of each connected to each of the connection protrusions; and an output rotator provided with a pair of connection protrusions protruding on opposite sides. An input rotator that is provided with a coupling structure and rotates integrally with the output rotator, and adjusts the engine phase between the crankshaft and the camshaft according to the control torque input from the output rotator to the input rotator. A phase adjustment mechanism, and each connection structure is fixed on the inner peripheral side of the main body member so that it is formed with higher hardness than the cylindrical main body member of the input rotating body and is substantially parallel to the radial direction of the main body member A pair of mating members, each connecting protrusion is characterized by being connected to the input rotary member than to fit between a pair of mating members of the corresponding connecting structure.

  As described above, according to the first aspect of the present invention, the pair of connecting protrusions protruding on the opposite sides in the radial direction in the output rotating body of the torque generating means are the pair of connecting protrusions provided on the output rotating body of the phase adjusting mechanism. Each is connected to a connecting structure. Here, each connecting projection is fitted between a pair of fitting members that are substantially parallel to the radial direction of the main body member in the corresponding connecting structure, but these fitting members are more than the cylindrical main body member of the input rotating body. Is also formed with high hardness and is fixed to the inner peripheral side of the main body member. Therefore, even if the fitting member that forms the fitting clearance and the coupling protrusion slide relative to each other due to an axial deviation or inclination between the input rotating body and the output rotating body, the fitting member having high hardness Is hard to wear. Therefore, not only can the connection work between the input rotating body and the output rotating body at the time of assembly be facilitated by securing the fitting clearance to increase the productivity, but also a decrease in durability due to wear of the fitting member and Generation of abnormal noise can be suppressed.

  According to invention of Claim 2, each fitting member has substantially the same hardness as each connection protrusion. According to this, even if the fitting member and the connecting projection that form the fitting clearance between each other slide relative to each other due to an axial deviation or an inclination between the input rotating body and the output rotating body, both wear. It becomes difficult to do. Therefore, it is possible to suppress a decrease in durability and the generation of abnormal noise due to wear of the fitting member and the connecting protrusion.

  According to invention of Claim 3, each connection structure has a connection body formed by connecting between a pair of fitting members by a connection member. According to this, since a pair of fitting members can be fixed to the main body member as a single connecting body rather than individually, the fixing work is facilitated and productivity is increased. .

  According to the invention described in claim 4, the coupling body is formed by connecting one end of each fitting member in the axial direction of the main body member by the connecting member, and is accommodated in the fixed recess opened to the inner peripheral side of the main body member. Fixed. According to this, on the inner peripheral side of the input rotating body in which the connecting body of each connecting structure is fixed to the main body member, the arrangement space of the output rotating body in which each connecting protrusion is connected to these connecting structures is made as much as possible. Large in size. Therefore, it is possible to contribute to the improvement of durability by forming the output rotator that rotates integrally with the input rotator on the outer peripheral side in the radial direction and increasing its strength.

  According to the fifth aspect of the present invention, the connecting body is press-fitted into the fixed recess of the main body member. According to this, the coupling body can be accommodated and fixed in the fixing recess of the main body member by a relatively simple operation such as press-fitting, so that productivity is improved.

  According to the sixth aspect of the present invention, the input rotating body is formed by press-fitting the connecting body from the connecting member side into the fixed recess that opens in the axial direction of the main body member. As described above, when the connecting body is press-fitted from the side reinforced by the connecting member into the fixed recess that opens in the axial direction of the main body member, deformation of the connecting body can be suppressed. Therefore, the fitting clearance between the fitting member of the coupling body press-fitted into the fixed recess and the coupling protrusion is accurately set, and the deterioration of durability due to wear and the generation of abnormal noise are reliably suppressed. It can be done.

  According to the seventh aspect of the present invention, the end portions of the fitting members on the side opposite to the connection member and the fixing recesses open to the torque generating means side in the axial direction of the main body member. According to this, the connection protrusion of the said means can be inserted from the torque generation means side of the axial direction of a main body member between each fitting member of the connection body accommodated and fixed by the fixed recessed part. Therefore, the connection work between the input rotating body and the output rotating body at the time of assembly can be facilitated, and productivity can be improved.

  According to the invention described in claim 8, the phase adjusting mechanism includes a first rotating body that rotates in conjunction with the crankshaft, a second rotating body that rotates in conjunction with the camshaft, a first rotating body, and a second rotating body. A planetary gear that changes the relative phase between the crankshaft and the camshaft by making a planetary motion while meshing with the gear portion, and a main body member that allows the planetary gear to freely move in planetary motion. And a planet carrier as an input rotating body to support. According to this, in order to change the engine phase between the crankshaft and the camshaft rotating in conjunction with the first and second rotating bodies with high responsiveness, the planets meshed with at least one gear portion of the rotating bodies. In order to make the planetary movement of the gear smooth, dimensional accuracy is required for the support portion of the planetary gear in the planetary carrier. Here, the planetary carrier serving as the input rotator only needs to have a high hardness for the fitting member of each connection structure with respect to the main body member that supports the planetary gear. Therefore, it is possible to avoid a situation in which the dimensional accuracy of the main body member that supports the planetary gear is deteriorated by heat treatment for increasing the hardness of the main body member.

  Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. In addition, the overlapping description is abbreviate | omitted by attaching | subjecting the same code | symbol to the corresponding component in each embodiment.

(First embodiment)
FIG. 2 shows a valve timing adjusting apparatus 1 according to the first embodiment of the present invention. The valve timing adjusting device 1 is mounted on a vehicle and installed in a transmission system that transmits engine torque from a crankshaft (not shown) of an internal combustion engine to a camshaft 2. The valve timing adjusting device 1 combines the electric drive system 4 and the phase adjusting mechanism 8 and adjusts the engine phase between the crankshaft and the camshaft 2 that determines the valve timing. In the present embodiment, the camshaft 2 opens and closes an intake valve (not shown) of the internal combustion engine, and the valve timing adjusting device 1 adjusts the valve timing of the intake valve.

  First, the electric drive system 4 will be described. The electric drive system 4 includes an electric motor 5 and an energization control circuit 6.

  The electric motor 5 is, for example, a brushless motor or the like, and generates a control torque output from the rotating shaft body 7 by energization. The energization control circuit 6 includes, for example, a microcomputer and a motor driver, and is disposed outside and / or inside the electric motor 5. The energization control circuit 6 is electrically connected to the electric motor 5 and controls energization to the electric motor 5 in accordance with the operation status of the internal combustion engine. In response to this controlled energization, the electric motor 5 holds or increases or decreases the control torque output from the rotating shaft body 7.

  Next, the phase adjustment mechanism 8 will be described. The phase adjusting mechanism 8 includes a driving side rotating body 10, a driven side rotating body 20, a planet carrier 40, and a planetary gear 50.

  As shown in FIGS. 2 to 4, the drive-side rotator 10 is formed by screwing a gear member 12 and a sprocket 13 both having a bottomed cylindrical shape on the same axis. The peripheral wall portion of the gear member 12 forms a drive-side internal gear portion 14 having a tip circle on the inner peripheral side of the root circle. The sprocket 13 is provided with a plurality of teeth 16 protruding outward in the radial direction. The sprocket 13 is linked to the crankshaft by winding an annular timing chain (not shown) between the teeth 16 and a plurality of teeth of the crankshaft. Therefore, when the engine torque output from the crankshaft is input to the sprocket 13 through the timing chain, the drive side rotator 10 rotates in conjunction with the crankshaft while maintaining a relative phase with respect to the crankshaft. At this time, the rotation direction of the drive side rotating body 10 is the counterclockwise direction of FIGS.

  As shown in FIGS. 2 and 3, the driven-side rotator 20 has a bottomed cylindrical shape and is concentrically disposed on the inner peripheral side of the sprocket 13. The peripheral wall portion of the driven-side rotator 20 forms a driven-side internal gear portion 22 having a tip circle on the inner peripheral side of the root circle.

  As shown in FIG. 2, the bottom wall portion of the driven-side rotator 20 forms a connecting portion 24 that is coaxially bolted to the cam shaft 2 and connected. Due to the connection between the connecting portion 24 and the cam shaft 2, the driven side rotating body 20 can rotate while maintaining a relative phase with respect to the cam shaft 2 in conjunction with the cam shaft 2. On the other hand, it is relatively rotatable. The relative rotational direction in which the driven-side rotator 20 advances with respect to the drive-side rotator 10 is the direction X in FIGS. 3 and 4, and the driven-side rotator 20 is retarded with respect to the drive-side rotator 10. The relative rotation direction is the direction Y in FIGS.

  As shown in FIG. 2, the planetary carrier 40 has a cylindrical shape as a whole, and an input wall 42 to which control torque is input from the rotating shaft 7 of the electric drive system 4 is formed on one end side. The rotating shaft 7 is connected to the input wall 42 concentric with the rotating bodies 10 and 20. By this connection, the planet carrier 40 can rotate integrally with the rotating shaft 7 and can rotate relative to the rotating bodies 10 and 20.

  As shown in FIGS. 2 to 4, the planetary carrier 40 further has a support wall 44 whose outer peripheral surface is eccentric with respect to the rotating bodies 10 and 20 on the end side opposite to the input wall 42. The support wall 44 is fitted to the inner peripheral side of the center hole 51 of the planetary gear 50 via a rolling bearing 45. By this fitting, the support wall 44 supports the planetary gear 50 so that the planetary gear 50 can move freely. Here, the planetary motion of the planetary gear 50 refers to the motion of the planetary gear 50 that revolves around the eccentric axis of the outer peripheral surface of the support wall 44 and revolves in the rotation direction of the support wall 44.

  The planetary gear 50 has a stepped cylindrical shape and is disposed concentrically with respect to the support wall 44. With this arrangement, the planetary gear 50 is always eccentric with respect to the gear portions 14 and 22 of the rotating bodies 10 and 20. In the planetary gear 50, a driving-side external gear portion 52 and a driven-side external gear portion 54 whose tip circles are on the outer peripheral side of the root circle are formed by a large-diameter portion and a small-diameter portion, respectively. The drive side external gear portion 52 is disposed on the inner peripheral side of the drive side internal gear portion 14 and meshes with the gear portion 14. The driven side external gear portion 54 is disposed on the inner peripheral side of the driven side internal gear portion 22 and meshes with the gear portion 22.

  With the above-described configuration, the phase adjustment mechanism 8 is formed with a differential gear type planetary mechanism 60 that decelerates the rotational motion of the planet carrier 40 and transmits it to the camshaft 2. The phase adjusting mechanism 8 having such a planetary mechanism unit 60 adjusts the engine phase according to the control torque input from the rotating shaft 7 to the planet carrier 40, so that the valve timing suitable for the internal combustion engine is obtained. Is realized.

  Specifically, when the planetary carrier 40 does not rotate relative to the drive-side rotator 10 due to the control torque being maintained or the like, the planetary gear 50 maintains the meshing position with the gear portions 14 and 22, while the rotator 10 and 20 rotate together. Therefore, the engine phase does not change, and as a result, the valve timing is kept constant.

  When the planetary carrier 40 rotates relative to the drive side rotor 10 in the direction X due to an increase in the control torque in the direction X or the like, the planetary gear 50 changes the meshing position with the gear portions 14 and 22 and performs planetary motion. As a result, the driven-side rotator 20 rotates relative to the drive-side rotator 10 in the direction X. Therefore, the engine phase changes to the advance side, and as a result, the valve timing advances.

  When the planetary carrier 40 rotates relative to the drive side rotor 10 in the direction Y due to an increase in the control torque in the direction Y or the like, the planetary gear 50 changes the meshing position with the gear portions 14 and 22 and performs planetary motion. As a result, the driven-side rotator 20 rotates relative to the drive-side rotator 10 in the direction Y. Therefore, the engine phase changes to the retard side, and as a result, the valve timing is retarded.

  Next, the characteristic part of 1st embodiment is demonstrated in detail. As shown in FIGS. 2 and 5, the rotating shaft 7 of the electric motor 5 is configured by combining a shaft member 70 and a joint member 72.

  The shaft member 70 is made of metal and has a straight round bar shape. The shaft member 70 receives the control torque generated by the electric motor 5 and rotates in the circumferential direction.

  The joint member 72 is made of metal, and is formed, for example, by sintering a copper-containing alloy steel powder and performing a heat treatment. As shown in FIGS. 1 and 5, the joint member 72 integrally forms a sleeve portion 74 and a connecting projection 76. The sleeve portion 74 has a cylindrical shape and is concentrically disposed on the inner peripheral side of the input wall 42 of the planet carrier 40. One end portion of the shaft member 70 is loosely inserted on the inner peripheral side of the sleeve portion 74. A connection pin 78 is fitted in the sleeve portion 74 and the shaft member 70 in the radial direction, so that the joint member 72 can rotate integrally with the shaft member 70. A pair of connection protrusions 76 are provided so as to protrude from the sleeve part 74 to opposite sides in the radial direction. Each connection protrusion 76 has a rectangular column shape in a plan view in the axial direction of the sleeve portion 74 (see FIG. 1).

  As shown in FIGS. 1 and 5, the planetary carrier 40 is provided with a pair of connection structures 90 respectively connected to the connection protrusions 76 on the main body member 80 that forms the input wall 42 and the support wall 44.

  The main body member 80 is made of metal, and is formed, for example, by sintering copper-containing alloy steel powder. The main body member 80 has a cylindrical shape as a whole, and has a pair of fixed recesses 82 that open to the inner periphery thereof. As shown in FIGS. 5 and 6, the fixed recesses 82 face each other in the radial direction of the main body member 80 and have a rectangular groove shape extending in the entire axial direction of the main body member 80. Therefore, any one end 84 side of each fixing recess 82 is open to the electric motor 5 (see FIG. 5) side in the axial direction of the main body member 80.

  As shown in FIGS. 1, 5, and 7, each connection structure 90 includes a connection body 92 that is fixed to the inner peripheral side of the main body member 80. The connecting body 92 is made of metal, has a hardness higher than that of the main body member 80, and has substantially the same hardness as the joint member 72. Here, the hardness of the coupling body 92 is set to be HRC55 or higher for the main body member 80 having hardness of HRC15 and the joint member 72 having hardness of HRC55 or higher, for example. In addition, the connecting body 92 that achieves such hardness is formed, for example, by subjecting a molded product obtained by forging high-carbon chromium bearing steel to heat treatment, specifically, quenching and annealing.

  As shown in FIG. 6, the coupling body 92 of each coupling structure 90 has a U-shape as a whole, and the fitting portion 94 and the connection portion 96 are integrally formed. As shown in FIGS. 1, 5, and 7, a pair of fitting portions 94 are provided so as to be substantially parallel to the radial direction and the axial direction of the main body member 80. Here, each fitting portion 94 has a rectangular flat plate shape in a plan view (see FIG. 5) in a direction orthogonal to the radial direction and the axial direction of the main body member 80. As shown in FIG. 6, the connection portion 96 connects between one end portions 98 of the fitting portions 94 in the axial direction of the main body member 80, and has a rectangular flat plate shape in a plan view (see FIG. 1) in the axial direction. Presents.

  As shown in FIGS. 5 and 7, the coupling bodies 92 of the coupling structures 90 are press-fitted into the corresponding fixing recesses 82. With this press-fitting, the coupling body 92 has the fitting portions 94 in close contact with the side walls 86 and the bottom walls 88 of the corresponding fixing recesses 82, and the end portion 99 opposite to the connection portion 96 in the fitting portions 94 is between the main body. The member 80 is housed and fixed in the concave portion 82 in a state where the member 80 opens toward the electric motor 5 (see FIG. 5) in the axial direction. As shown in FIGS. 1 and 5, the coupling protrusions 76 are fitted between the fitting portions 94 of the coupling body 92 in such a fixed state, whereby the joint member 72 of the rotating shaft body 7 and the main body of the planetary carrier 40. The member 80 is connected to be integrally rotatable.

  According to the first embodiment described above, the pair of connecting projections 76 provided on the rotating shaft body 7 are fitted between the fitting parts 94 that are substantially parallel in the connecting body 92 of the corresponding connecting structure 90. Thus, it is connected to the planet carrier 40. Here, since the hardness of the fitting portion 94 is higher than the hardness of the main body member 80 constituting the majority of the planet carrier 40 and is substantially the same as the hardness of the connecting projection 76, the fitting clearance is formed between them. Even if the joint portion 94 and the connecting projection portion 76 slide relative to each other due to an axial deviation or inclination between the rotating elements 7 and 40, they are not easily worn. Therefore, not only can the connecting work between the rotating elements 7 and 40 at the time of assembly be facilitated by securing the fitting clearance to increase the productivity, but also the elements 94 and 76 that are interfitted wear. It is possible to suppress deterioration of durability and occurrence of abnormal noise.

  In addition, according to the first embodiment, as each connecting structure 90, a connecting body 92 formed by connecting the pair of fitting portions 94 fitted to the connecting protrusion 76 by the connecting portion 96 is a fixing recess 82 of the main body member 80. Therefore, the fixing work can be facilitated and productivity can be increased. In addition, according to the first embodiment, the fitting portions 94 of the coupling body 92 are connected to each other at the one end 98 side in the axial direction of the main body member 80, and the fixed recess 82 that opens to the inner peripheral side of the main body member 80 Since the coupling body 92 is housed and fixed, the inner circumferential space of the planet carrier 40 becomes as large as possible. Therefore, it is possible to increase the durability by forming the joint member 72 of the rotating shaft body 7 arranged on the inner peripheral side of the planetary carrier 40 in the radial direction and increasing its strength.

  Further, for example, as shown by a one-dot chain line arrow in FIG. 6, in the first embodiment, the connecting member 96 is reinforced from the reinforced connecting part 96 side with respect to the fixed recessed part 82 opened to the electric motor 5 side in the axial direction of the main body member 80. By press-fitting 92, deformation of the coupling body 92 can be suppressed. In this case, since the fitting clearance between the fitting portion 94 of the connecting body 92 press-fitted into the fixed recess 82 and the connecting protrusion 76 can be set accurately, it results from the wear of these elements 94 and 76. It is possible to reliably suppress the deterioration of durability and the generation of abnormal noise.

  Furthermore, according to the first embodiment, the gap between the pair of fitting portions 94 fitted to the connection protrusions 76 in the connection body 92 of each connection structure 90 is on the side opposite to the electric motor 5 in the axial direction of the main body member 80. Although connected, the electric motor 5 side is open with the fixed recess 82. Therefore, it is possible to easily connect the rotating elements 7 and 40 by inserting the connecting protrusion 76 from the electric motor 5 side between the fitting portions 94 of the connecting body 92 fixed to the inner peripheral side of the main body member 80. Can increase productivity.

  In addition, according to the first embodiment, in order to change the engine phase between the crankshaft and the camshaft 2 that rotate in conjunction with the driving side and driven side rotating bodies 10 and 20 with high responsiveness, the rotating bodies 10 and 20 It is necessary to make the planetary movement of the planetary gear 50 meshing with the 20 gear portions 14 and 22 smooth. Here, in order to make the planetary movement of the planetary gear 50 smooth, it is required to increase the dimensional accuracy of the support part of the planetary gear 50 in the planetary carrier 40. In the planetary carrier 40 of the first embodiment, although the main body member 80 that supports the planetary gear 50 by the support wall 44 is made of metal, a high-hardness connecting body 92 is adopted separately from the main body member 80, so There is no need to heat-treat the main body member 80 for increasing the hardness. Therefore, it is possible to avoid the situation where the dimensional accuracy of the main body member 80 that supports the planetary gear 50 by the support wall 44 is deteriorated by the heat treatment for increasing the hardness, and to improve the response of the engine phase to the control torque of the electric motor 5. Can do it.

  In the first embodiment, the electric motor 5 corresponds to the “torque generating means” described in the claims, the rotary shaft body 7 corresponds to the “output rotating body” described in the claims, and the planets. The carrier 40 corresponds to an “input rotator” recited in the claims. The fitting portion 94 corresponds to a “fitting member” recited in the claims, and the connection portion 96 corresponds to a “connecting member” recited in the claims. Further, the driving side rotating body 10 corresponds to the “first rotating body” described in the claims, the driven side rotating body 20 corresponds to the “second rotating body” described in the claims, and the driving side The internal gear portion 14 and the driven side internal gear portion 22 correspond to an “internal gear portion” recited in the claims.

(Second embodiment)
As shown in FIGS. 8 and 9, the second embodiment of the present invention is a modification of the first embodiment. In the second embodiment, the coupling body 102 of each coupling structure 100 has a U-shape as a whole, but the end portions 108 of the fitting portions 104 in the radial direction of the main body member 80 are connected by the connection portion 106. It has become a thing.

  Therefore, in a state where the coupling body 102 is housed and fixed in the fixed recess 82 by press-fitting as shown in FIG. 8, the fitting portions 104 are in close contact with the side wall 86 and the bottom wall 88 of the recess 82, and the fitting portions 104. The space is open on both sides of the main body member 80 in the axial direction. Therefore, also according to the second embodiment, the rotating elements 7 and 40 are inserted by inserting the connecting protrusion 76 from the electric motor 5 side between the fitting portions 104 of the connecting body 102 fixed to the inner peripheral side of the main body member 80. Since the gaps can be easily connected, productivity is increased.

  In the second embodiment, the fitting portion 104 corresponds to a “fitting member” recited in the claims, and the connection portion 106 corresponds to a “connecting member” recited in the claims.

(Third embodiment)
As shown in FIGS. 10 and 11, the third embodiment of the present invention is a modification of the first embodiment. In the third embodiment, each connection structure 200 is configured such that the connection portion 96 is removed from the connection body 92 of the first embodiment, and only the pair of fitting members 204 corresponding to the pair of fitting portions 94 is provided. ing. Therefore, the pair of fitting members 204 of each connection structure 200 are fixed or substantially parallel to each other on the inner peripheral side of the main body member 80 by being bonded or welded to the side wall 86 and the bottom wall 88 of the corresponding fixing recess 82. ing.

  Therefore, in a state where the pair of fitting members 204 of each coupling structure 200 is housed and fixed in the fixing recess 82 as shown in FIG. 10, the shape between the fitting members 204 opens on both sides in the axial direction of the main body member 80. It becomes. Therefore, also by 3rd embodiment, between the fitting members 204 fixed to the main body member 80, the connection protrusion 76 is inserted from the electric motor 5 side, so that the rotation elements 7 and 40 can be easily connected. Because it can, productivity is increased.

(Other embodiments)
Although a plurality of embodiments of the present invention have been described above, the present invention is not construed as being limited to these embodiments, and can be applied to various embodiments without departing from the scope of the present invention. .

  Specifically, in the first to third embodiments, if the coupling bodies 92 and 102 or the fitting member 204 have a hardness higher than that of the main body member 80, for example, a high carbon is used without performing a heat treatment for increasing the hardness. You may form only by forging of chromium bearing steel. Conversely, in the first to third embodiments, the main body member 80 is obtained by sintering copper-containing alloy steel powder, for example, if the hardness is lower than that of the coupling bodies 92, 102 or the fitting member 204. The fired product may be subjected to heat treatment for increasing the hardness. Furthermore, in 1st-3rd embodiment, if the coupling member 72 which has the connection protrusion 76 is substantially the same hardness as the connection bodies 92 and 102 or the fitting member 204, it will not perform the heat processing for high hardness. For example, you may form only by sintering of a copper containing alloy steel powder.

  In addition, in the first and second embodiments, according to the third embodiment, the coupling bodies 92 and 102 may be accommodated and fixed in the fixing recess 82 by adhesion or welding. In the third embodiment, an individual fixing recess may be provided for each fitting member 204, and each fitting member 204 may be press-fitted and fixed in the individual fixing recess.

  In addition, in the first to third embodiments, the rotating shaft body 7 formed by fixing the joint member 72 to the shaft member 70 may be employed. Alternatively, in the first to third embodiments, the rotary shaft body 7 in which the connection protrusion 76 is directly formed on the shaft member 70 may be employed.

  In addition, in the first to third embodiments, for example, an electric brake or a hydraulic motor such as an electromagnetic brake or a fluid brake may be employed as the “torque generating means”. In the first to third embodiments, various phase adjusting mechanisms can be employed as long as the effects of the present invention can be obtained. For example, a planetary gear is meshed with a gear portion provided on one of two rotating bodies that rotate in conjunction with the crankshaft and the camshaft, and the other of the rotating bodies is connected to the planetary gear. A phase adjustment mechanism or the like that changes the engine phase by being rotationally driven by planetary motion may be employed.

  The present invention can be applied not only to a device that adjusts the valve timing of the intake valve, but also to a device that adjusts the valve timing of the exhaust valve and a device that adjusts the valve timing of both the intake valve and the exhaust valve. it can.

It is a figure which shows the principal part of the valve timing adjustment apparatus by 1st embodiment of this invention, Comprising: It is the II sectional view taken on the line of FIG. It is a figure which shows the valve timing adjustment apparatus by 1st embodiment of this invention, Comprising: It is the II-II sectional view taken on the line of FIG. It is the III-III sectional view taken on the line of FIG. It is the IV-IV sectional view taken on the line of FIG. It is the VV sectional view taken on the line of FIG. It is a disassembled perspective view which shows the principal part of the valve timing adjustment apparatus by 1st embodiment of this invention. It is a perspective view which shows the principal part of the valve timing adjustment apparatus by 1st embodiment of this invention. It is a perspective view which shows the principal part of the valve timing adjustment apparatus by 2nd embodiment of this invention. It is a disassembled perspective view which shows the principal part of the valve timing adjustment apparatus by 2nd embodiment of this invention. It is a perspective view which shows the principal part of the valve timing adjustment apparatus by 3rd embodiment of this invention. It is a disassembled perspective view which shows the principal part of the valve timing adjustment apparatus by 3rd embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Valve timing adjustment apparatus, 2 cam shaft, 4 Electric drive system, 5 Electric motor (torque generation means), 7 Rotating shaft body (output rotating body), 8 Phase adjustment mechanism, 10 Drive side rotating body (1st rotating body) , 14 Drive side internal gear part (gear part), 20 Drive side rotary body (second rotary body), 22 Drive side internal gear part (gear part), 40 Planet carrier (input rotary body), 42 Input wall, 44 Support Wall, 50 planetary gear, 70 shaft member, 72 joint member, 74 sleeve portion, 76 connecting protrusion, 78 connecting pin, 80 body member, 82 fixing recess, 90, 100, 200 connecting structure, 92, 102 connecting body, 94 104, fitting part (fitting member), 96, 106 connecting part (connecting member), 98 one end part, 99 opposite end part, 204 fitting member

Claims (8)

A valve timing adjusting device that adjusts the valve timing of at least one of an intake valve and an exhaust valve that opens and closes a camshaft by torque transmission from a crankshaft in an internal combustion engine,
A torque generating means for generating a control torque output from the output rotating body, the output rotating body having a pair of connecting protrusions protruding on opposite sides in the radial direction;
The control torque input from the output rotator to the input rotator is provided with a pair of linking structures respectively connected to the connection protrusions and having an input rotator that rotates integrally with the output rotator. And a phase adjustment mechanism for adjusting a relative phase between the crankshaft and the camshaft according to
Each of the connection structures is formed with a higher hardness than the cylindrical main body member of the input rotating body and is fixed to the inner peripheral side of the main body member so as to be substantially parallel to the radial direction of the main body member. Having a fitting member,
Each said connection protrusion is connected with the said input rotary body by fitting between said pair of fitting members of the said corresponding connection structure, The valve timing adjustment apparatus characterized by the above-mentioned.   The valve timing adjusting device according to claim 1, wherein each of the fitting members has substantially the same hardness as each of the connection protrusions.   3. The valve timing adjusting device according to claim 1, wherein each of the connection structures includes a connection body formed by connecting the pair of fitting members with a connection member. 4.   The connecting body is configured such that one end of each fitting member in the axial direction of the main body member is connected by the connecting member, and is accommodated and fixed in a fixing recess that opens to the inner peripheral side of the main body member. 4. The valve timing adjusting device according to claim 3, wherein   The valve timing adjusting device according to claim 4, wherein the connecting body is press-fitted into the fixed recess.   6. The valve timing adjusting device according to claim 5, wherein the input rotating body is configured such that the connecting body is press-fitted from the connecting member side into the fixed recess that opens in the axial direction of the main body member.   The space between the end portions of each fitting member opposite to the connection member and the fixing recess are open to the torque generating means side in the axial direction of the main body member. The valve timing adjusting device according to claim 1.   The phase adjusting mechanism includes at least one of a first rotating body that rotates in conjunction with the crankshaft, a second rotating body that rotates in conjunction with the camshaft, and the first rotating body and the second rotating body. As a gear portion provided on one side, a planetary gear that changes the relative phase by planetary movement while meshing with the gear portion, and the input rotating body that supports the planetary gear in a planetary motion by the main body member It has a planetary carrier, The valve timing adjustment apparatus as described in any one of Claims 1-7 characterized by the above-mentioned.

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