A phase adjuster with a locking mechanism

Abstract

The present invention discloses a phase adjuster with a locking mechanism, belonging to the technical field of camshaft phase adjusters. It mainly arranges a limiting tooth and a limiting groove that cooperate with each other, so that after the driving motor fails, the limiting tooth can be reset to the initial phase under the drive of the resistance torque of the camshaft and abut against the end of the limiting groove. At the same time, a locking mechanism is provided to limit the rotation of the input part relative to the sprocket when the input part has a tendency to rotate in the advance angle direction due to the alternating sinusoidal resistance torque of the camshaft, so that the camshaft can be relatively stable at the initial phase.

Description

Technical Field

[0001] The present invention relates to the technical field of camshaft phase adjusters, and in particular to a phase adjuster with a locking mechanism. Background Art

[0002] The camshaft phase adjuster is a device used to adjust the rotation angle of the camshaft relative to the crankshaft. It can control the timing of valve opening and closing to improve the efficiency of the gas engine. At present, the phase adjuster can be divided into two types: electric phase adjuster and hydraulic phase adjuster according to different operating modes. Among them, the conventional electric phase adjuster is mainly composed of: a sprocket that rotates in the driving direction with the crankshaft through a chain, and a reduction gear pair whose active end is connected to the drive motor and whose output end is fixedly connected to the camshaft. For this kind of electric phase adjuster, since its output end can rotate arbitrarily, once the motor fails and can no longer provide driving torque, the crankshaft cannot drive the camshaft to rotate, resulting in engine failure.

[0003] Therefore, in the subsequent electric phase adjusters, the positive gear reduction pair is mainly used as the reduction pair, and a limited position structure is arranged between the output end and the active end, and the two can only rotate at a limited angle to ensure that after the motor fails, the output end can be reset to the initial phase under the action of the resistance torque provided by the camshaft and the motor, and is directly driven by the sprocket to rotate through the limited structure. However, this electric phase adjuster also has certain defects, which is mainly because the resistance torque transmitted to the output end by the camshaft is an alternating sinusoidal shape. Therefore, after the output end is reset to the initial phase, the alternating resistance torque of the camshaft will drive the output end to swing back and forth, increasing the noise and vibration of the engine. Summary of the invention

[0004] In summary, the technical problem solved by the present invention is to provide a phase adjuster that can keep the camshaft in an initial phase more stably when the motor fails.

[0005] The solution adopted by the present invention to solve the above technical problems is:

[0006] A phase regulator with a locking mechanism includes a sprocket that rotates synchronously with the crankshaft, an output part coaxially and rotatably connected inside the sprocket and fixedly connected coaxially with the camshaft, and an input part connected to the motor. The sprocket, the output part, and the input part are axially fixed and form a reduction gear pair, so that the rotation of the motor can drive the output part to rotate relative to the sprocket in the advance angle or retard angle direction. The inner circumferential surface of the sprocket is configured with a limiting groove extending along its circumference and closed at both ends. The output part forms a limiting tooth extending radially therefrom and extending into the limiting groove. At the initial phase, one end of the limiting tooth and the limiting groove abuts. It further includes a locking mechanism. The locking mechanism includes a torsion spring. The torsion spring includes a first leg and a second leg extending radially therefrom and offset from each other. At the initial phase, the first leg acts on the sprocket, and the second leg acts on the input part. When the input part rotates due to the resistance moment of the camshaft, the two legs of the torsion spring elastically twist to apply a torque to the input part, thereby restricting its rotation.

[0007] Further, the input part includes: a main gear disposed inside the sprocket, a sun gear coaxially disposed with the sprocket and rotatable about its own axis driven by the driving motor, a plurality of planet gears circumferentially spaced along the sun gear and meshing with the sun gear, and an eccentric shaft corresponding to the planet gear; an internal tooth extending along the circumference is provided on the inner circumference of the sprocket, and the main gear meshes with the internal tooth, and the number of teeth of the main gear is less than the number of teeth of the internal tooth; the axis of the planet gear is parallel to the axis of the sprocket, the coaxial part of the eccentric shaft is fixedly connected coaxially with the corresponding planet gear, the eccentric shaft penetrates through both the main gear and the output part at the same time, and the eccentric part of the eccentric shaft is rotatably connected to the main gear, so that the rotation of the eccentric shaft can drive the main gear to perform a planetary motion around the axis of the sprocket, and the coaxial part of the eccentric shaft is rotatably connected to the output part.

[0008] Further, the torsion spring is connected to the front end face of the sprocket, and its axis is parallel to the axis of the sprocket. The torsion spring is located radially outside the planet gear. At the initial phase, the second leg extends into the tooth space between the planet gears and abuts against the planet gear. The second leg can abut against the tooth tip of the planet gear as the planet gear rotates, so that the torsion spring applies a torque to restrict the rotation of the planet gear.

[0009] Further, at the initial phase, elastic torsion occurs between the second leg and the first leg, and as the planet gear rotates, the second leg elastically restores.

[0010] Furthermore, the torsion spring can rotate around its own axis relative to the sprocket, the first leg is slidably connected to the sprocket, and has a first limiting position and a second limiting position sequentially distributed along the circumferential direction of the torsion spring; at the initial phase, the first leg is in the first limiting position, and as the planetary gear rotates, the first leg is driven by the planetary gear to move from the first limiting position to the second limiting position, and the first limiting position is closer to the planetary gear than the second limiting position.

[0011] Furthermore, a chute extending along the circumferential direction of the torsion spring is formed on the front end face of the sprocket, both ends of the chute are closed, the end of the first leg is bent and extends into the chute, and can slide along the extending direction of the chute.

[0012] Furthermore, the locking mechanism further includes a rotating pin coaxially inserted into the torsion spring and relatively rotatable with the torsion spring, one end of the rotating pin is inserted into the sprocket, the other end of the rotating pin forms a limiting flange, and the limiting flange and the front end face of the sprocket together limit the axial displacement of the torsion spring located between the two.

[0013] Furthermore, the output part is mainly composed of an output flange cover and a support flange cover arranged in sequence along its axis, the output flange cover is used to be connected with the camshaft, the output flange cover and the support flange cover are fixedly connected, and there is a space between them in the axial direction, so as to form a receiving space for receiving the main gear, and the end faces of both ends of the main gear are respectively in sliding contact with the end faces of the output flange cover and the support flange cover.

[0014] Furthermore, a ring-shaped flange protruding and extending into the receiving space is formed on the inner circumference of the sprocket, the ring-shaped flange is clamped between the end faces of the output flange cover and the support flange cover, the internal teeth are arranged on the inner circumference of the ring-shaped flange, and a first support ring surface in rotational contact with the outer circumference of the output flange cover and a second support ring surface in rotational contact with the outer circumference of the support flange cover are formed on the inner circumference of the sprocket.

[0015] Furthermore, the eccentric shaft is simultaneously inserted into the output flange cover and the support flange cover, and its coaxial parts are respectively rotationally connected with the output flange cover and the support flange cover.

[0016] In summary, due to the adoption of the above technical solutions, the beneficial effects of the present invention are as follows: by arranging the mutually cooperating limiting teeth and limiting grooves, after the driving motor fails, the limiting teeth can be reset to the initial phase under the driving of the resistance torque of the camshaft and abut against the end of the limiting groove. At the same time, a locking mechanism is provided to limit the rotation of the input part relative to the sprocket when the input part has a tendency to rotate in the advance angle direction due to the alternating sinusoidal resistance torque of the camshaft, so that the camshaft can be relatively stable at the initial phase. Description of the Drawings

[0017] Figure 1 Structural schematic diagram of Embodiment 1 of the present invention;

[0018] Figure 2 Front view of Embodiment 1 of the present invention;

[0019] Figure 3 is Figure 2 Cross-sectional view taken along line A-A in

[0020] Figure 4 is Figure 3 Cross-sectional view taken along line B-B in

[0021] Figure 5 Structural schematic diagram of the first support ring surface, the second support ring surface and the annular flange in Embodiment 1 of the present invention;

[0022] Figure 6 Structural schematic diagram of the support flange cover and the output flange cover in Embodiment 1 of the present invention;

[0023] Figure 7 Structural schematic diagram of the eccentric shaft in Embodiment 1 of the present invention;

[0024] Figures 8 to 10 Schematic diagram of the cooperation of the limiting groove, the limiting teeth and the like in Embodiment 1 of the present invention;

[0025] Figure 11 and Figure 12 Schematic diagram of the positions of the torsion spring and the planetary gear at the initial phase in Embodiment 1 of the present invention;

[0026] Figure 13 and Figure 14 Schematic diagram of the interaction between the planetary gear and the torsion spring when the planetary gear rotates at the initial phase in Embodiment 1 of the present invention;

[0027] Figure 15 and Figure 16 Structural schematic diagram of the torsion spring in Embodiment 1 of the present invention.

[0028]

Specific symbol description

[0029] 1 - Sprocket, 101 - Annular flange, 102 - Internal teeth, 103 - First support ring surface, 104 - Second support ring surface, 2 - Main gear, 3 - Output part, 301 - Output flange cover, 302 - Support flange cover, 4 - Sun gear, 5 - Planetary gear, 6 - Eccentric shaft, 601 - Eccentric part, 602 - Coaxial part, 7 - Connecting boss, 8 - Connecting screw, 9 - Movable clearance, 10 - Camshaft, 11 - Limiting teeth, 12 - Limiting groove, 13 - Torsion spring, 14 - First foot, 15 - Second foot, 16 - Slide groove, 17 - Rotating pin, 18 - Motor rotating shaft, 19 - Camshaft connecting screw. Detailed implementation mode

[0030] The following will introduce in detail a phase regulator with a locking mechanism provided by the present invention in conjunction with the accompanying drawings and embodiments.

[0031] Embodiment 1

[0032] As Figures 1 to 16 shown, a phase regulator with a locking mechanism provided in Embodiment 1 of the present invention includes a sprocket 1 that can rotate synchronously with the crankshaft, an output portion 3 coaxially and rotatably connected inside the sprocket 1 and fixedly connected to the camshaft 10 coaxially, and an input portion connected to the motor. The sprocket 1, the output portion 3, and the input portion are axially fixed and form a reduction gear pair, so that the rotation of the motor can drive the output portion 3 to rotate relative to the sprocket 1 in the advance angle or retard angle direction. A limiting groove 12 extending along the circumferential direction of the sprocket 1 and closed at both ends is formed on the inner circumferential surface of the sprocket 1. The output portion 3 forms a limiting tooth 11 extending radially and extending into the limiting groove 12. At the initial phase, one end of the limiting tooth 11 abuts against the limiting groove 12. It further includes a locking mechanism. The locking mechanism includes a torsion spring 13. The torsion spring 13 includes a first leg 14 and a second leg 15 extending radially and offset from each other. At the initial phase, the first leg 14 acts on the sprocket 1, while the second leg 15 acts on the input portion. When the input portion rotates due to the resistance torque of the camshaft 10, the two legs of the torsion spring 13 elastically twist to apply a torque to the input portion, thereby restricting its rotation.

[0033] In the stage of motor failure, the input portion loses the input action of driving the motor. At this time, relative to the sprocket 1, the resistance torque of the camshaft 10 will drive the output portion 3 coaxially connected to the camshaft 10 to rotate in the retard angle direction. Specifically, the resistance torque of the input portion received by the camshaft 10 is in an alternating sine shape, and the absolute value of the maximum value of the resistance torque in the advance angle direction is less than the absolute value of the maximum value of the resistance torque in the retard angle direction. Therefore, after the motor fails, the output portion 3 generally has a tendency to rotate in the retard angle direction.

[0034] And when the camshaft 10 and the crankshaft return to the initial phase, as Figures 8 to 10As shown in the figure, the limit tooth 11 on the output part 3 abuts against one end of the limit groove 12, thereby restricting the rotational movement of the output part 3. At the same time, as described in the background art part above, since the resistance torque of the camshaft 10 acting on the output part 3 is an alternating sine wave, when it returns to the initial phase, it will swing back and forth at the initial phase. At this time, the torsion spring 13 in the locking mechanism acts between the input part and the sprocket 1, applying a torque to the input part to overcome the resistance torque of the camshaft 10 it receives, thereby restricting the rotation of the output part 3 in the advance angle direction and the rotation of the input part. The entire camshaft 10 together with the input part can be relatively stably in the initial phase, reducing the noise and vibration of the entire engine.

[0035] Among them, the above-mentioned advance angle direction refers to: the rotational direction of the output part 3 relative to the sprocket 1 with the phase advancing forward; while the lag angle direction is opposite to the advance angle direction, specifically referring to: the rotational direction of the output part 3 relative to the sprocket 1 with the phase lagging backward.

[0036] At the same time, as Figures 1 to 7 shown, in Embodiment 1 of the present invention, the input part includes: a main gear 2 disposed inside the sprocket 1, a sun gear 4 coaxially disposed with the sprocket 1 and capable of rotating self - rotatably under the drive of a drive motor, a plurality of planet gears 5 circumferentially spaced along the sun gear 4 and meshing with the sun gear 4, and an eccentric shaft 6 corresponding to the planet gears 5; an internal tooth 102 extending along the circumferential direction is provided on the inner circumference of the sprocket 1, the main gear 2 meshes with the internal tooth 102, and the number of teeth of the main gear 2 is less than the number of teeth of the internal tooth 102; the axis of the planet gear 5 is parallel to the axis of the sprocket 1, the coaxial part 602 of the eccentric shaft 6 is coaxially fixedly connected with the corresponding planet gear 5, the eccentric shaft 6 passes through both the main gear 2 and the output part 3 at the same time, and the eccentric part 601 of the eccentric shaft 6 is rotatably connected with the main gear 2, so that the self - rotation of the eccentric shaft 6 can drive the main gear 2 to perform a planetary motion around the axis of the sprocket 1, and the coaxial part 602 of the eccentric shaft 6 is rotatably connected with the output part 3. Among them, the input part, the sprocket 1 and the output part 3 form a positive gear reduction pair.

[0037] Specifically, as Figure 3 shown, in the normal use state, the sun gear 4 driven by the motor shaft 18 rotates synchronously with the sprocket 1, so the two can be regarded as relatively stationary, and the phase of the camshaft 10 does not change; while in the state of adjusting the phase of the camshaft 10, the rotational speed of the sun gear 4 is faster or slower than that of the sprocket 1; at this time, the self - rotation of the sun gear 4 drives the self - rotation of the eccentric shaft 6, and the main gear 2 starts to perform a planetary motion around the axis of the sprocket 1 relying on the self - rotation action of the eccentric shaft 6.

[0038] During the planetary motion of the main gear 2, the eccentric shaft 6 that penetrates the main gear 2 and the driven part simultaneously drives the entire driven part to rotate, thereby realizing the phase adjustment of the camshaft 10 fixedly connected coaxially with the driven part.

[0039] Among them, it can be understood that, as Figure 7 shown, the eccentric shaft 6 is mainly composed of an eccentric part 601 and a coaxial part 602. The axis of the eccentric part 601 is parallel to but does not coincide with the axis of the coaxial part 602. The correspondence between the eccentric shaft 6 and the planetary gear 5 means that the two are consistent in quantity and correspond one by one.

[0040] At the same time, as Figure 11 and Figure 12 shown, the schematic diagram at the initial phase. In the first embodiment, the torsion spring 13 is connected to the front end face of the sprocket 1, and its axis is parallel to the axis of the sprocket 1. The torsion spring 13 is located radially outside the planetary gear 5; at the initial phase, the second leg 15 extends into the tooth gap of the planetary gear 5 and abuts against the planetary gear 5. The second leg 15 can abut against the tooth top of the planetary gear 5 as the planetary gear 5 rotates, so that the torsion spring 13 applies a torque to the planetary gear 5 to restrict its rotation. Specifically, at the initial phase, since one end of the limit tooth 11 and the limit groove 12 abuts, the entire planetary gear 5 can only rotate in the direction of driving the output part 3 along the lag angle, as Figure 13 and Figure 14 shown. When the planetary gear 5 rotates, it abuts against the second leg 15, causes the second leg 15 to disengage from the tooth gap, and acts on its tooth top, thereby causing an elastic torsion closer to the first leg 14. It can be understood that the second leg 15 undergoes the largest torsional deformation at the tooth top. At this time, the torque it applies to the planetary gear 5 is also the largest. Its value is greater than the maximum value of the resistance torque that the planetary gear 5 receives and causes it to drive the input part to rotate in the direction of the advance angle.

[0041] The first embodiment mainly acts on the input part of the entire phase adjuster. This is because as a speed reduction mechanism, the input part of the phase adjuster receives a relatively small resistance torque from the camshaft 10. Therefore, it is easier to lock the torsion spring 13 acting on the planetary gear 5, and the design requirements are lower.

[0042] To ensure that the second leg 15 can effectively extend into the tooth gap of the planetary gear 5 at the initial phase, as a preferred embodiment, in the first embodiment, at the initial phase, an elastic torsion occurs between the second leg 15 and the first leg 14, and as the planetary gear 5 rotates, the second leg 15 undergoes elastic recovery. Among them, as Figure 12As shown, at this time, an elastic torsion away from each other occurs between the second leg 15 and the first leg 14. The purpose of this setting is as follows: during the phase callback stage, at the same time, since the planetary gear 5 has two rotational motions, namely revolution and rotation, the second leg 15 will pass through some tooth tops of the planetary gear 5. No matter how it passes through the tooth tops, it will always elastically reset after passing through and act between the tooth gaps, and will not stay at the tooth tops, so that the second leg 15 can more easily extend into the tooth gaps of the planetary gear 5 at the initial phase.

[0043] In another embodiment, the first leg 14 of the torsion spring 13 is fixedly connected to the sprocket 1, and the above functions can also be achieved. However, considering the limited performance of the existing torsion spring 13, if the first leg 14 is directly fixed to the sprocket 1, the second leg 15 is prone to excessive elastic torsion under the action of the planetary gear 5, thus causing the failure of the torsion spring 13. Therefore, in the present Embodiment 1, the torsion spring 13 can rotate around its own axis relative to the sprocket 1, the first leg 14 is slidably connected to the sprocket 1, and it has a first limit position and a second limit position that are sequentially distributed along the circumferential direction of the torsion spring 13; at the initial phase, the first leg 14 is in the first limit position, and as the planetary gear 5 rotates, the first leg 14 is driven by the planetary gear 5 to move from the first limit position to the second limit position, and the first limit position is closer to the planetary gear 5 than the second limit position.

[0044] At the initial phase, when the planetary gear 5 starts to rotate and before the torsion spring 13 undergoes elastic torsion, first, it will drive its first leg 14 to move to the second limit position under the drive of the planetary gear 5. Since the first limit position is closer to the planetary gear 5 than the second limit position, and the second leg 15 gradually moves away from the planetary gear 5 during the braking process of the planetary gear 5, so compared with the case where the first leg 14 is fixed, when the rotation of the input part stops, the deformation amount of the elastic torsion of mutual approach between the first leg 14 and the second leg 15 is reduced, thereby effectively improving the stability of the torsion spring 13.

[0045] More specifically, as Figure 11 shown, in the present Embodiment 1, a chute 16 extending along the circumferential direction of the torsion spring 13 is provided on the front end face of the sprocket 1. Both ends of the chute 16 are closed. The end of the first leg 14 is bent and extends into the chute 16 and can slide along the extending direction of the chute 16. Among them, when the first leg 14 abuts against both ends of the chute 16 respectively, it is in the first limit position and the second limit position respectively. In other embodiments, two limit blocks are provided on the front end face of the sprocket 1 at intervals along the circumferential direction of the torsion spring 13. The first leg 14 is placed between the two limit blocks, and when it abuts against the two limit blocks respectively, it is in the first limit position and the second limit position respectively.

[0046] More specifically, as Figures 15 to 16 shown, in Embodiment 1, the ends of the first supporting leg 14 and the second supporting leg 15 are bent in an L shape. The bent portion of the first supporting leg 14 extends into the sliding groove 16, while the bent portion of the second supporting leg 15 is used to contact the tooth portion of the planetary gear 5, thereby improving the stability of applying force to the planetary gear 5.

[0047] Furthermore, in Embodiment 1, the locking mechanism further includes a rotating pin 17 coaxially inserted into the torsion spring 13 and capable of relatively rotating with the torsion spring 13. One end of the rotating pin 17 is inserted into the sprocket 1, and the other end of the rotating pin 17 forms a limiting flange. The limiting flange and the front end face of the sprocket 1 together limit the axial displacement of the torsion spring 13 located therebetween.

[0048] As a preferred embodiment, as Figure 5 and Figure 6 shown, in Embodiment 1, the output portion 3 is mainly composed of an output flange cover 301 and a support flange cover 302 arranged in sequence along its axial direction. The output flange cover 301 is used to connect with the camshaft 10. The output flange cover 301 and the support flange cover 302 are fixedly connected, and there is a gap between them in the axial direction, thereby forming a receiving space for receiving the main gear 2. The end faces of both ends of the main gear 2 are in sliding contact with the end faces of the output flange cover 301 and the support flange cover 302 respectively, so that relative sliding can occur between the main gear 2 and the output flange cover 301, and between the main gear 2 and the support flange cover 302.

[0049] More specifically, in Embodiment 1, the specific structure for realizing the relative fixation of the sprocket 1, the output portion 3, and the main gear 2 in the axial direction is as follows: a ring-shaped flange 101 protruding and extending into the receiving space is formed on the inner circumference of the sprocket 1, and the ring-shaped flange 101 is clamped between the end faces of the output flange cover 301 and the support flange cover 302.

[0050] Wherein, in Embodiment 1, the internal teeth 102 are provided on the inner circumference of the ring-shaped flange 101. A first support ring surface 103 in rotational contact with the outer circumference of the output flange cover 301 and a second support ring surface 104 in rotational contact with the outer circumference of the support flange cover 302 are formed on the inner circumference of the sprocket 1 to respectively support and rotatably connect the output flange cover 301 and the support flange cover 302. More specifically, the output portion 3 is mainly composed of an output flange cover 301 and a support flange cover 302 arranged in sequence along its axial direction. The output flange cover 301 is used to connect with the camshaft 10. The output flange cover 301 and the support flange cover 302 are fixedly connected, and there is a gap between them in the axial direction, thereby forming a receiving space for receiving the main gear 2. The end faces of both ends of the main gear 2 are in sliding contact with the end faces of the output flange cover 301 and the support flange cover 302 respectively.

[0051] It is understandable that if Figure 7 As shown, the eccentric shaft 6 is mainly composed of an eccentric portion 601 and a coaxial portion 602, and the axis of the eccentric portion 601 is parallel to but not coincident with the axis of the coaxial portion 602. Therefore, as long as the eccentric shaft 6 is inserted into one of the output flange cover 301 or the support flange cover 302, the eccentric shaft 6 can drive the entire output portion 3 to rotate.

[0052] The output flange cover 301 is coaxially connected to the camshaft 10 mainly through the camshaft connecting screws 19 .

[0053] However, during the specific implementation, we found that: since the eccentric shaft 6 mainly relies on its eccentric portion 601 to drive the entire main gear 2 to perform planetary motion, and the eccentric portion 601 applies radial force to the main gear 2, it itself will also be subjected to a reaction force; and if the eccentric shaft 6 is only inserted into one of the output flange cover 301 or the support flange cover 302, the eccentric shaft 6 is prone to side deviation and displacement.

[0054] As a preferred embodiment, in this embodiment 1, if Figure 3 As shown, the eccentric shaft 6 is inserted into the output flange cover 301 and the support flange cover 302 at the same time, and its coaxial portion 602 is rotatably connected to the output flange cover 301 and the support flange cover 302 respectively. That is to say, in this embodiment 1, the coaxial portion 602 of the eccentric shaft 6 is divided into two sections, and the eccentric portion 601 is connected between the two sections of the coaxial portion 602. The two sections of the eccentric shaft 6 are respectively inserted into the output flange cover 301 and the support flange cover 302, and each is rotatably connected to the corresponding flange cover. During operation, the support flange cover 302 and the output flange cover 301 respectively provide support forces for overcoming the resistance of the main gear 2, thereby improving the support stability and support strength of the eccentric shaft 6.

[0055] In this embodiment 1, the output flange cover 301 and the support flange cover 302 are fixedly connected by a plurality of connection structures disposed between the two and penetrating the main gear 2. The plurality of connection structures are disposed at intervals along the circumference of the output portion 3. The implementer can make an adaptive selection from the existing technology. As a preferred embodiment, in this embodiment 1, if Figure 4 and Figure 6As shown, the connection structure mainly consists of a connection boss 7 that is integrally formed with the output flange cover 301 and penetrates through the main gear 2, and a connection screw 8 that penetrates through the support flange cover 302 and is threadedly connected to the connection boss 7, so as to ensure the stable connection between the support flange cover 302 and the output flange cover 301. At the same time, since the main gear 2 makes a planetary motion around the axes of the sprocket 1 and the output part 3 once, a relative translation in the radial direction will occur between the main gear 2 and the output part 3. Therefore, in this Embodiment 1, a movable gap 9 is left between the connection boss 7 and the main gear 2 to avoid interference between the two.

Claims

1. A phase adjuster with a locking mechanism, comprising a sprocket that can rotate synchronously with the crankshaft, an output part coaxially and rotationally connected inside the sprocket and fixedly connected coaxially with the camshaft, and an input part connected to the motor. The sprocket, the output part, and the input part are axially fixed and form a reduction gear pair, so that the rotation of the motor can drive the output part to rotate relative to the sprocket in the advance angle or retard angle direction. Characterized in that: The inner circumferential surface of the sprocket is configured with a limiting groove extending along its circumferential direction and closed at both ends. The output part forms a limiting tooth extending radially therefrom and extending into the limiting groove. At the initial phase, one end of the limiting tooth and the limiting groove abuts. It also includes a locking mechanism. The locking mechanism includes a torsion spring. The torsion spring includes a first leg and a second leg extending radially therefrom and offset from each other. At the initial phase, the first leg acts on the sprocket, and the second leg acts on the input part. When the input part rotates due to the resistance torque of the camshaft, the two legs of the torsion spring elastically twist to apply a torque to the input part, thereby restricting its rotation. The input part includes: a main gear disposed inside the sprocket, a sun gear coaxially disposed with the sprocket and capable of rotating self - driven by the driving motor, a plurality of planet gears circumferentially spaced along the sun gear and meshing with the sun gear, and an eccentric shaft corresponding to the planet gear. An internal tooth extending along the circumferential direction is provided on the inner circumference of the sprocket. The main gear meshes with the internal tooth, and the number of teeth of the main gear is less than that of the internal tooth. The axis of the planet gear is parallel to the axis of the sprocket. The coaxial part of the eccentric shaft is coaxially and fixedly connected with the corresponding planet gear. The eccentric shaft penetrates into both the main gear and the output part at the same time. The eccentric part of the eccentric shaft is rotationally connected with the main gear, so that the self - rotation of the eccentric shaft can drive the main gear to perform a planetary motion around the axis of the sprocket. The coaxial part of the eccentric shaft and the output part are rotationally connected. The torsion spring is connected to the front end face of the sprocket, and its axis is parallel to the axis of the sprocket. The torsion spring is located radially outside the planet gear. At the initial phase, the second leg extends into the tooth space of the planet gear and abuts against the planet gear. The second leg can elastically twist and abut against the tooth top of the planet gear as the planet gear rotates, so that the torsion spring applies a torque to restrict the rotation of the planet gear.

2. A phase adjuster with a locking mechanism according to claim 1, Characterized in that: At the initial phase, elastic torsion occurs between the second leg and the first leg, and as the planet gear rotates, the second leg elastically restores.

3. A phase adjuster with a locking mechanism according to claim 1, Characterized in that: The torsion spring can rotate around its own axis relative to the sprocket. The first leg is slidably connected to the sprocket and has a first limiting position and a second limiting position sequentially distributed along the circumferential direction of the torsion spring. At the initial phase, the first leg is in the first limiting position. As the planet gear rotates, the first leg is driven by the planet gear to move from the first limiting position to the second limiting position. The first limiting position is closer to the planet gear than the second limiting position.

4. A phase adjuster with a locking mechanism as claimed in claim 3, characterized in that: a chute extending in the circumferential direction of the torsion spring is formed on the front end face of the sprocket, both ends of the chute are closed, the end of the first leg is bent and extends into the chute, and can slide along the extending direction of the chute.

5. A phase adjuster with a locking mechanism as claimed in claim 3, characterized in that: the locking mechanism further includes a rotating pin coaxially inserted into the torsion spring and capable of relatively rotating with the torsion spring, one end of the rotating pin is inserted into the sprocket, the other end of the rotating pin forms a limiting flange, and the limiting flange and the front end face of the sprocket together limit the axial displacement of the torsion spring located between the two.

6. A phase adjuster with a locking mechanism as claimed in claim 1, characterized in that: the output part is mainly composed of an output flange cover and a support flange cover arranged in sequence along its axis, the output flange cover is used to connect with the camshaft, the output flange cover and the support flange cover are fixedly connected, and there is a distance between them in the axial direction, so as to form a receiving space for receiving the main gear, and the end faces of both ends of the main gear are in sliding contact with the end faces of the output flange cover and the support flange cover respectively.

7. A phase adjuster with a locking mechanism as claimed in claim 6, characterized in that: a ring-shaped flange protruding and extending into the receiving space is formed on the inner circumference of the sprocket, the ring-shaped flange is clamped between the end faces of the output flange cover and the support flange cover, the internal teeth are arranged on the inner circumference of the ring-shaped flange, and a first support ring surface in rotational contact with the outer circumference of the output flange cover and a second support ring surface in rotational contact with the outer circumference of the support flange cover are formed on the inner circumference of the sprocket.

8. A phase adjuster with a locking mechanism as claimed in claim 6, characterized in that: the eccentric shaft is simultaneously inserted into the output flange cover and the support flange cover, and its coaxial parts are respectively rotationally connected with the output flange cover and the support flange cover.

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