JP2016053332A - Camshaft phase continuous variable driving device for internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a camshaft phase continuous variable driving device of which compact formation can be easily carried out.SOLUTION: This invention comprises a pair of bevel gears 11, 12 arranged between a camshaft driving gear 4 and a camshaft 5; a connecting shaft 3 passing through central round holes 11a, 12a of the bevel gears 11, 12 so as to connect the camshaft driving gear 4 with the camshaft 5 in helical spline connection; a bevel pinion 13 engaged between the bevel gears 11, 12; and solenoid brakes 16, 17 for bevel gears so as to reduce speed of rotation of the bevel gears 11, 12. A right female thread 11b is formed in a central round hole 11a, a left female thread 12b is formed in the central round hole 12a. The outer periphery of the connecting shaft 3 is formed with a right male thread 23 engaged in thread with the right female thread 11b of the first bevel gear 11 and a left male thread 24 engaged in thread with the left female thread 12b of the second bevel gear 12, and a location of the connecting shaft 3 that can be positioned between the bevel gears 11, 12 are formed with the right male thread 23 and the left male thread 24 overlapped to each other.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a camshaft phase continuously variable drive device for an internal combustion engine.

  Conventionally, in an internal combustion engine, the camshaft phase continuously variable drive device is used to change the camshaft rotation phase to the advance or retard direction, thereby adjusting the opening and closing timings of the intake valve and the exhaust valve, thereby improving the fuel efficiency and It is known to improve emission and torque-rotation characteristics (see, for example, Patent Document 1).

JP-A-7-279632

  By the way, there are many cases where the arrangement space of the internal combustion engine is limited, such as an engine room of an automobile, and therefore, it is desired to make the cam shaft phase continuously variable drive device compact. However, in the camshaft phase continuously variable drive device described in Patent Document 1, the camshaft phase continuously variable drive device is arranged between the pair of bevel gears because the camshaft drive gear interlocked with the crankshaft of the internal combustion engine is disposed between the pair of bevel gears. Protrudes outward from the camshaft drive gear. As a result, it is difficult to make the camshaft phase continuously variable drive device compact.

  Therefore, it is conceivable that the camshaft drive gear is arranged at a position deviated from between the bevel gears so as to narrow the separation distance between the bevel gears, but the portion of the connecting shaft that meshes with one bevel gear is the other bevel gear. Cannot be engaged with each other, so that the range of movement of the connecting shaft in the axial direction is limited, and the rotational phase of the camshaft cannot be sufficiently changed.

  The present invention has been made in view of the above-described circumstances, and an object of the present invention is to provide a cam shaft phase continuously variable drive device that can be easily made compact.

The present invention has been proposed in order to achieve the above object. According to the first aspect of the present invention, a camshaft is rotated by a rotational force received by a transmission vehicle from a crankshaft side of an internal combustion engine. In the cam shaft phase continuously variable drive device that changes the rotation phase of the shaft,
A pair of bevel gears disposed between the transmission wheel and the camshaft and rotatably supported with the gear surfaces facing each other;
A connecting shaft that passes through a central circular hole established for each of the bevel gears, and connects the transmission wheel and the camshaft by helical spline coupling;
A bevel pinion meshed between opposing gear surfaces of the bevel gear;
A bevel gear brake means attached to each of the bevel gears to decelerate the rotation of the bevel gear;
With
A right female thread is formed in the central circular hole of one bevel gear, a left female thread is formed in the central circular hole of the other bevel gear,
On the outer periphery of the connecting shaft, a right male screw that is screwed to the right female screw of one bevel gear and a left male screw that is screwed to the left female screw of the other bevel gear are formed.
A cam shaft phase continuously variable drive device for an internal combustion engine, wherein the right male screw and the left male screw are overlapped and formed at a position that can be located at least between the bevel gears on the outer periphery of the connecting shaft. is there.

  According to a second aspect of the present invention, in the internal combustion engine cam shaft phase continuously variable drive device according to the first aspect, the bevel gear brake means comprises an electromagnetic brake.

According to a third aspect of the present invention, each of the bevel gears includes a mysterious planetary gear mechanism configured by meshing a planetary gear with a pair of ring gears having different numbers of teeth.
The wonder planetary gear mechanism is characterized in that one of the pair of ring gears is connected to the bevel gear so as to rotate together, and the ring gear brake means is attached to the other ring gear. 2. A cam shaft phase continuously variable drive device for an internal combustion engine according to 2.

According to a fourth aspect of the present invention, a rough phasing operation for changing the rotational phase of the camshaft by shifting the phase of the rotating bevel gears by executing the operation of the bevel gear brake means;
After the coarse phasing operation, the ring gear brake means is operated to shift the phases of the rotating bevel gears, thereby changing the rotational phase of the camshaft at a slower speed than the coarse phasing operation. Operation and
The cam shaft phase continuously variable drive device for an internal combustion engine according to claim 3, wherein:

  According to a fifth aspect of the present invention, in the internal combustion engine cam shaft phase continuously variable drive device according to the third or fourth aspect, the ring gear brake means comprises an electromagnetic brake.

According to the present invention, the following excellent effects can be obtained.
According to the first aspect of the present invention, a pair of bevel gears disposed between the transmission vehicle and the camshaft and rotatably supported with the gear surfaces facing each other, and each bevel gear is provided. A connecting shaft that penetrates the central circular hole and connects the transmission vehicle and the camshaft by helical spline coupling, a bevel pinion that is meshed between the gear surfaces facing each other of the bevel gear, and each bevel gear is attached. A bevel gear brake means for decelerating the rotation of the bevel gear, wherein a right female screw is formed in the central circular hole of one bevel gear, and a left female screw is formed in the central circular hole of the other bevel gear, and the connecting shaft A right male screw that is screwed to the right female screw of one bevel gear and a left male screw that is screwed to the left female screw of the other bevel gear are formed on the outer periphery of the bevel gear. Since the right male screw and the left male screw are formed so as to overlap each other at a position that can be located between the bevel gears, the distance between the bevel gears is reduced without limiting the axial movement range of the connecting shaft. be able to. Therefore, it is easy to make the camshaft phase continuously variable drive device compact.

  According to the second aspect of the present invention, since the bevel gear brake means is an electromagnetic brake, the bevel gear brake means can be realized with a simple configuration. Moreover, the bevel gear can be decelerated without any delay by energization.

  According to a third aspect of the present invention, each of the bevel gears includes a wonder planetary gear mechanism configured by meshing a planetary gear with a pair of ring gears having different numbers of teeth. Since one of the pair of ring gears is connected to the bevel gear in a co-rotating state, and the other ring gear is provided with a ring gear brake means, the other ring gear is rotated by the operation of the ring gear brake means. When the speed is reduced, the rotation of the bevel gear that rotates together with one of the ring gears is gradually reduced as compared with the operation of the bevel gear brake means. For this reason, in changing the rotational phase of the camshaft, it is possible to perform fine adjustments that are difficult to reduce by the deceleration by the bevel gear brake means, thereby improving the accuracy of changing the rotational phase.

  According to the fourth aspect of the present invention, the rough phase determining operation for changing the rotational phase of the camshaft by executing the operation of the brake means for the bevel gear and shifting the phases of the rotating bevel gears, A precise phasing operation that changes the rotational phase of the camshaft at a slower speed than the coarse phasing operation by executing the operation of the ring gear brake means after the phasing operation and shifting the phases of the rotating bevel gears. Therefore, the rotational phase of the camshaft can be changed quickly and accurately.

  According to the fifth aspect of the present invention, since the ring gear brake means is an electromagnetic brake, the ring gear brake means can be realized with a simple configuration. Further, by energizing, the ring gear can be decelerated, and thus the bevel gear can be decelerated without delay.

It is a schematic sectional drawing of a cam shaft phase continuous variable drive device. It is a schematic sectional drawing of the cam shaft phase continuous variable drive device provided with the mysterious planetary gear mechanism. It is a partial expanded sectional view of the camshaft phase continuous variable drive device provided with the mysterious planetary gear mechanism. It is a timing chart of operation | movement of the cam shaft phase continuous variable drive device provided with the mysterious planetary gear mechanism.

Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings.
As shown in FIG. 1, a camshaft phase continuously variable drive device 1 provided in an internal combustion engine is a device configured by penetrating a connecting shaft 3 through a differential gear portion 2, and from a crankshaft via a chain ( A camshaft drive gear 4 (corresponding to a transmission vehicle in the present invention) that receives rotational force and a cam 5a that controls the opening / closing timing of an intake valve or an exhaust valve (both not shown) are provided. It is arranged between the cam shaft 5. Then, the camshaft drive gear 4 and the camshaft 5 are connected by the connecting shaft 3, and the camshaft 5 is rotated by the rotational force received by the camshaft drive gear 4, or the rotational phase of the camshaft 5 is changed. It is configured as follows. The camshaft drive gear 4 and the camshaft 5 are rotatably supported on the cylinder head side of the internal combustion engine. The internal combustion engine is provided with a rotation phase detection sensor (not shown) that detects the rotation phase of the camshaft 5.

  The differential gear portion 2 includes a gear case 10 disposed in a cylinder head (not shown) of the internal combustion engine, and a pair of bevel gears (first bevel gear 11 and second bevel gear 12) housed in the gear case 10. The bevel gears 11 and 12 are provided with a bevel pinion 13 disposed between the bevel gears 11 and 12. Specifically, a pair of bevel gears 11 and 12 are rotatably supported by bearings 14a and 14b in the gear case 10 with the gear surfaces facing each other, and the bevel gears 11 and 12 are opposed to each other between the opposing gear surfaces. A plurality of bevel pinions 13 (for example, three bevel pinions 13 arranged with phases shifted by 120 degrees around the rotation axis of the bevel gears 11 and 12) are meshed. In the schematic cross-sectional view shown in FIG. 1, the bevel pinion 13 is drawn so as to appear above and below the connecting shaft 3 for convenience. An annular pinion support 15 that is slightly larger than the outer periphery of the bevel gears 11 and 12 is disposed so as to cover the gap between the pair of bevel gears 11 and 12 from the outside, and each bevel pinion 13 is attached to the pinion support 15. Is supported in a rotatable state. Then, central circular holes 11a and 12a are formed at the rotation centers of the bevel gears 11 and 12, respectively, in the central circular hole 11a of the first bevel gear 11 located on the camshaft drive gear 4 side (left side in FIG. 1). Forms a right female thread 11b, and a left female thread 12b is formed in the central circular hole 12a of the second bevel gear 12 located on the camshaft 5 side (right side in FIG. 1).

  Further, between each bevel gear 11, 12 and the gear case 10, an electromagnetic brake (first bevel gear electromagnetic brake 16, second bevel gear electromagnetic brake 17) functioning as a bevel gear brake means is provided for each bevel gear 11, 12. Each is attached. The first bevel gear for the first bevel gear is based on a control signal from a control device (not shown) that controls the operation of the camshaft phase continuously variable drive device 1 while the bevel gears 11 and 12 are rotating during operation of the internal combustion engine. When the electromagnetic brake 16 is energized, a brake pad (not shown) of the first bevel gear electromagnetic brake 16 is moved by an electromagnetic force and is brought into pressure contact with the outer surface of the first bevel gear 11 to decelerate the rotation of the first bevel gear 11. Is configured to do. When the second bevel gear electromagnetic brake 17 is energized, a brake pad (not shown) of the second bevel gear electromagnetic brake 17 is moved by electromagnetic force and is brought into pressure contact with the outer surface of the second bevel gear 12. The rotation of the bevel gear 12 is configured to decelerate. Furthermore, a phase shift detection sensor (not shown) such as a rotation pulse sensor capable of detecting a shift in the rotation phase of the first bevel gear 11 is provided in the vicinity of the first bevel gear electromagnetic brake 16 in the gear case 10. The detection signal of the deviation detection sensor can be transmitted to the control device.

  The connecting shaft 3 connects the camshaft drive gear 4 and the camshaft 5 in a state of passing through the central circular holes 11a and 12a of both the bevel gears 11 and 12. Further, a left-hand-side gear-side helical spline protrusion 21 is engraved on the outer peripheral surface of the gear-side end portion (left end portion in FIG. 1) connected to the camshaft drive gear 4, By engaging the gear-side helical spline protrusion 21 with a helical spline groove 4a formed in a left-hand threaded state, the connecting shaft 3 and the camshaft drive gear 4 are coupled (helical spline coupled in a left-handed thread state). Yes. Further, a camshaft-side helical spline protrusion 22 in a right-hand thread state is provided on the outer peripheral surface of the camshaft side end portion (right end portion in FIG. 1) connected to the camshaft 5, The connecting shaft 3 and the camshaft 5 are coupled (helical spline coupling in the right-hand thread state) by engaging the camshaft-side helical spline protrusion 22 with the helical spline groove 5b formed in the right-hand thread state. Therefore, the rotational phase of the cam shaft 5 with respect to the cam shaft drive gear 4 is shifted when the connecting shaft 3 moves to the cam shaft 5 side or to the cam shaft drive gear 4 side.

  Specifically, when the combined body including the cam shaft 5, the connecting shaft 3, and the cam shaft driving gear 4 is viewed from the cam shaft 5 side (right side in FIG. 1), the connecting shaft 3 is moved to the cam shaft 5 side. The connecting shaft 3 shifts the rotational phase in the clockwise direction with respect to the camshaft drive gear 4 by helical spline coupling in the left-handed state. Further, since the cam shaft 5 and the connecting shaft 3 are helically spline-coupled in a right-handed state, the cam shaft 5 shifts the rotational phase in the clockwise direction with respect to the cam shaft driving gear 4 more than the connecting shaft 3. On the other hand, when the connecting shaft 3 is moved to the camshaft drive gear 4 side, the connecting shaft 3 shifts the rotational phase in the counterclockwise direction with respect to the camshaft drive gear 4 by the left-handed helical spline coupling. Further, since the cam shaft 5 and the connecting shaft 3 are helically splined in a right-handed state, the cam shaft 5 shifts the rotational phase further counterclockwise than the connecting shaft 3 with respect to the cam shaft drive gear 4. . In this way, when the connecting shaft 3 moves along the axial direction, the cam shaft 5 is configured such that the rotational phase is shifted by the sum of the rotational amounts due to the two helical spline couplings.

  A right male screw 23 screwed into the right female screw 11 b of the first bevel gear 11 and a left female screw of the second bevel gear 12 are located at positions between the helical spline protrusions 21 and 22 on the outer periphery of the connecting shaft 3. A left male screw 24 that is screwed to 12b is formed. Specifically, a right male screw 23 is formed on the first bevel gear 11 side (left side in FIG. 1) of the outer peripheral portion, and a left male screw 24 is formed on the second bevel gear 12 side (right side in FIG. 1). Forming. Furthermore, a right male screw 23 and a left male screw 24 are formed so as to overlap each other at a position that can be positioned between the bevel gears 11 and 12 among the outer peripheral portions. In this overlapping formation portion, a parallelogram-like protrusion as viewed from the radial direction of the connecting shaft 3 is surrounded by a valley (spiral groove) adjacent to the right male screw 23 and a valley (spiral groove) adjacent to the left male screw 24. (If the pitch of the right male screw 23 and the pitch of the left male screw 24 are equal, a plurality of rhombus-shaped projections) are formed, and each projection is arranged along the spiral direction of the right male screw 23 and the spiral direction of the left male screw 24. Yes.

  Next, the operation of the camshaft phase continuously variable drive device 1 having such a configuration will be described. The camshaft drive gear 4 that receives the rotational force from the crankshaft during the operation of the internal combustion engine is clockwise as viewed from the camshaft 5 side (right side in FIG. 1), as indicated by an arrow in FIG. It shall rotate. Further, for convenience of explanation, when the rotation direction viewed from the cam shaft 5 side of the components of the cam shaft phase continuously variable drive device 1, the cam shaft 5 and the cam shaft drive gear 4 is described, it is simply “clockwise”. , Written as “counterclockwise”.

  When the crankshaft of the internal combustion engine rotates in a state in which none of the bevel gear electromagnetic brakes 16 and 17 is operating, the camshaft drive gear 4 receives the rotational force, and the connecting shaft 3 that is helically splined to the camshaft drive gear 4. The cam shaft 5 helically splined to the connecting shaft 3, the bevel gears 11, 12 meshing with the connecting shaft 3, and the bevel pinion 13 meshing the bevel gears 11, 12 rotate together in the clockwise direction. The exhaust valve or intake valve opens and closes based on the rotation of the cam 5a provided in the valve.

  When the control device operates only the first bevel gear electromagnetic brake 16 by energization in this co-rotation state, the first bevel gear 11 receives the braking force from the first bevel gear electromagnetic brake 16 and the rotation of the first bevel gear 11 is rotated by the camshaft. 5 and the camshaft drive gear 4. Further, the bevel pinion 13 rotates due to the deceleration of the rotation of the first bevel gear 11, and the rotation of the second bevel gear 12 that meshes with the bevel pinion 13 is increased by the deceleration of the rotation of the first bevel gear 11. Accordingly, the first bevel gear 11 shifts the rotational phase in the counterclockwise direction with respect to the rotating connecting shaft 3, while the second bevel gear 12 shifts the rotational phase in the clockwise direction so that the first bevel gear 11 and the second bevel gear 12 Is differential.

  Then, the coupling shaft 3 is connected to the camshaft by meshing between the right male screw 23 of the coupling shaft 3 and the right female screw 11b of the first bevel gear 11 and meshing between the left male screw 24 of the coupling shaft 3 and the left female screw 12b of the second bevel gear 12. It moves to the drive gear 4 side (left side in FIG. 1). As a result, the camshaft 5 is converted into a retarded state by shifting the rotation phase counterclockwise with respect to the camshaft drive gear 4 (in other words, the direction opposite to the rotation direction of the camshaft 5 (clockwise)). The operation timing of the valve by the cam 5a is delayed from the state before the operation of the first bevel gear electromagnetic brake 16. Then, the phase shift of the first bevel gear 11 detected by the phase shift detection sensor is a predetermined target value (specifically, the phase of the first bevel gear 11 necessary for realizing the target retarded state of the camshaft 5). ), The control device cuts off the power supply to the first bevel gear electromagnetic brake 16 based on the signal from the phase shift detection sensor, the braking operation of the first bevel gear 11 is released, and the camshaft drive gear 4 The connecting shaft 3, the cam shaft 5, the bevel gears 11 and 12, and the bevel pinions 13 rotate together in the retarded state.

  On the other hand, when the control device operates only the second bevel gear electromagnetic brake 17 by energization in the above-mentioned co-rotation state, the second bevel gear 12 receives the braking force from the second bevel gear electromagnetic brake 17 and the rotation of the second bevel gear 12 is caused. It decelerates from the camshaft 5 and the camshaft drive gear 4. Furthermore, the bevel pinion 13 rotates due to the deceleration of the rotation of the second bevel gear 12, and the rotation of the first bevel gear 11 that meshes with the bevel pinion 13 increases by the deceleration of the rotation of the second bevel gear 12. Accordingly, the second bevel gear 12 shifts the rotational phase in the counterclockwise direction with respect to the rotating connecting shaft 3, while the first bevel gear 11 shifts the rotational phase in the clockwise direction so that the first bevel gear 11 and the second bevel gear 12 Is differential.

  Then, the coupling shaft 3 is connected to the camshaft by meshing between the right male screw 23 of the coupling shaft 3 and the right female screw 11b of the first bevel gear 11 and meshing between the left male screw 24 of the coupling shaft 3 and the left female screw 12b of the second bevel gear 12. Move to the 5 side (right side in FIG. 1). As a result, the cam shaft 5 is converted into an advanced state by shifting the rotational phase in the clockwise direction relative to the cam shaft drive gear 4 (in other words, in the same direction as the rotation direction (clockwise direction) of the cam shaft 5). The operation timing of the valve is advanced from the state before the operation of the electromagnetic brake 17 for the second bevel gear. The phase shift of the first bevel gear 11 detected by the phase shift detection sensor is a predetermined target value (specifically, the phase of the first bevel gear 11 necessary for realizing the target advanced state of the camshaft 5). ), The control device cuts off the energization of the second bevel gear electromagnetic brake 17 based on the signal from the phase shift detection sensor, the braking operation of the second bevel gear 12 is released, and the camshaft drive gear 4 The connecting shaft 3, the cam shaft 5, the bevel gears 11 and 12, and the bevel pinions 13 rotate together in the advanced state.

  In the cam shaft phase continuously variable drive device 1 capable of performing such an operation, the right male screw 23 and the left male screw 24 are superimposed on a portion of the outer periphery of the connecting shaft 3 that can be positioned between the bevel gears 11 and 12. Therefore, the portion of the connecting shaft 3 that has been screwed to one bevel gear can be screwed to the other bevel gear when the connecting shaft 3 is moved. Accordingly, the distance between the bevel gears 11 and 12 can be made narrower than that of the conventional non-overlapping screw without limiting the axial movement range of the connecting shaft 3. Accordingly, it is easy to make the camshaft phase continuously variable drive device 1 compact. Further, since the electromagnetic brake (bevel gear electromagnetic brakes 16 and 17) is employed as the bevel gear brake means, the bevel gear brake means can be realized with a simple configuration. Further, the time delay from the energization of the bevel gear electromagnetic brakes 16 and 17 to the start of braking of the bevel gears 11 and 12 can be shortened. Therefore, the deceleration of the bevel gears 11 and 12 can be executed without delay by energization.

  By the way, in the said 1st Embodiment, although rotation of the bevel gears 11 and 12 was decelerated only by the electromagnetic brakes 16 and 17 for bevel gears, this invention is not limited to this. For example, in the cam shaft phase continuously variable drive device 1 ′ of the second embodiment shown in FIGS. 2 and 3, the basic configuration is the same as that of the first embodiment, but the bevel gear electromagnetic brakes 16 and 17 are the same. However, it is different in that the rotation of the bevel gears 11 'and 12' can be decelerated by the mysterious planetary gear mechanism.

  More specifically, each of the bevel gears 11 ′ and 12 ′ of the differential gear portion 2 ′ in the second embodiment has a strange planetary gear mechanism (first gear mechanism) that is a variable planetary gear mechanism as shown in FIGS. 1 wonder planetary gear mechanism 31 and second wonder planetary gear mechanism 32), and the center axes of the wonder planetary gear mechanisms 31, 32 are aligned with the rotation centers of the bevel gears 11 ′, 12 ′ and the rotation center of the connecting shaft 3. It is arranged. In the first bevel gear 11 ′, the cam gear driving gear 4 side (left side in FIG. 2) is recessed in an annular shape to form a first gear mechanism arrangement space portion 33, and the first gear mechanism arrangement space portion is formed. A first mysterious planetary gear mechanism 31 is arranged in the inside 33. Further, a central circular shaft 11a in which a central circular hole 11a is opened at the center portion surrounded by the annular first gear mechanism arrangement space 33 and the connecting shaft 3 meshes with the right female screw 11b on the inner peripheral surface. A meshing portion 34 is formed. Further, in the second bevel gear 12 ′, the cam shaft 5 side (right side in FIG. 2) is recessed in an annular shape to form a second gear mechanism arrangement space portion 37. The second mysterious planetary gear mechanism 32 is arranged on the front. Furthermore, a cylindrical second shaft in which a central circular hole 12a is opened at the center portion surrounded by the annular second gear mechanism arrangement space 37 and the connecting shaft 3 meshes with the left female screw 12b on the inner peripheral surface. A meshing portion 38 is formed.

  The first mysterious planetary gear mechanism 31 arranges a pair of ring gears (first inner ring gear 41 and first outer ring gear 42) having different numbers of teeth so as to overlap each other along the axial direction of the connecting shaft 3. A plurality of planetary gears (for example, the three first planetary gears 43 arranged with a phase difference of 120 degrees around the rotation axis of the ring gears 41, 42) are shared by the internal teeth of the pair of ring gears 41, 42. In this meshed state, each first planetary gear 43 is pivotally attached to a first carrier 44 formed in an annular shape around the rotation axis of the ring gears 41, 42, The relative positions of the one planetary gears 43 are kept constant. In the schematic cross-sectional view shown in FIG. 2, the first planetary gear 43 is drawn so as to appear above and below the connecting shaft 3 for convenience. In addition, a first sun gear 45 that loosely fits the first shaft meshing portion 34 inside is arranged at the center of the first mysterious planetary gear mechanism 31, and the first planetary gears 43 are meshed with the outer periphery. The first planetary gear 43 is configured to revolve along the outer periphery of 45. In the first sun gear 45, no force is transmitted between components other than the first planetary gear 43. Therefore, if the first planetary gear 43 can be sufficiently held by the first carrier 44, The first mysterious planetary gear mechanism 31 may be configured without providing one sun gear 45.

  Further, of the pair of ring gears 41 and 42, the first inner ring gear 41 located on the camshaft 5 side (right side in FIG. 2) is connected to the first bevel gear 11 'in a state of rotating together (for example, a bolt or the like). The first outer ring gear 42 located on the camshaft drive gear 4 side (left side in FIG. 2) is placed between the outer peripheral edge of the first gear mechanism arrangement space portion 33 and the first shaft meshing portion 34. The first and second bearings 46 and 47 are supported in a rotatable manner. The number of teeth of the first inner ring gear 41 is set to be larger than the number of teeth of the first outer ring gear 42 (for example, three more). Therefore, the first planetary gear 43 rotates (spins) while the first inner ring gear 41 and the first outer ring gear 42 are engaged with the common first planetary gear 43 to rotate both the ring gears 41 and 42. (Rotation) When the first outer ring gear 42 makes one rotation, the first inner ring gear 41 rotates less than one rotation by the number of teeth. Thereby, the rotation of the first inner ring gear 41 is configured to be slower than the rotation of the first outer ring gear 42.

  The second mysterious planetary gear mechanism 32 arranges a pair of ring gears (second inner ring gear 51 and second outer ring gear 52) having different numbers of teeth so as to overlap with each other along the axial direction of the connecting shaft 3. A plurality of planetary gears (for example, the three second planetary gears 53 arranged with a phase difference of 120 degrees around the rotation axis of the ring gears 51, 52) are shared by the internal teeth of the pair of ring gears 51, 52 In this meshing state, each second planetary gear 53 is pivotally attached to a second carrier 54 formed in an annular shape around the rotation axis of the ring gears 51 and 52, and the second planetary gear 53 is pivotally attached to the second carrier 54. The relative position between the two planetary gears 53 is kept constant. In the schematic cross-sectional view shown in FIG. 2, the second planetary gear 53 is drawn so as to appear above and below the connecting shaft 3 for convenience. In addition, a second sun gear 55 that loosely fits the second shaft meshing portion 38 inside is arranged at the center of the second mysterious planetary gear mechanism 32 so that each second planetary gear 53 meshes with the outer periphery. The second planetary gear 53 is configured to revolve along the outer periphery of 55. In the second sun gear 55, no force is transmitted between the components other than the second planetary gear 53. Therefore, if the second planetary gear 53 can be sufficiently held by the second carrier 54, The second mysterious planetary gear mechanism 32 may be configured without providing the two sun gears 55.

  Further, of the pair of ring gears 51 and 52, the second inner ring gear 51 located on the camshaft drive gear 4 side (left side in FIG. 2) is connected to the second bevel gear 12 'in a state of rotating together (for example, The second outer ring gear 52, which is fastened with a bolt or the like and is located on the camshaft 5 side (right side in FIG. 2), is located between the outer peripheral edge of the second gear mechanism arrangement space portion 37 and the second shaft meshing portion 38. Are supported in a freely rotatable manner via second bearings 56 and 57. The number of teeth of the second inner ring gear 51 is set to be larger than the number of teeth of the second outer ring gear 52 (for example, three more). Accordingly, the second planetary gear 53 rotates (spins) in a state where the second inner ring gear 51 and the second outer ring gear 52 are engaged with the common second planetary gear 53 to rotate both the ring gears 51 and 52. (Rotation) When the second outer ring gear 52 rotates once, the second inner ring gear 51 rotates less than one rotation by the number of teeth. Thereby, the rotation of the second inner ring gear 51 is configured to be slower than the rotation of the second outer ring gear 52.

  Further, between the outer ring gears 42 and 52 and the gear case 10, electromagnetic brakes (first ring gear electromagnetic brake 61 and second ring gear electromagnetic brake 62) functioning as ring gear brake means are provided outside. Each ring gear 42, 52 is attached. When the first ring gear electromagnetic brake 61 is energized based on a control signal from the control device while the outer ring gears 42 and 52 are rotating during the operation of the internal combustion engine, the first ring gear electromagnetic brake 61 is turned on. The brake pad is configured to be brought into pressure contact with the outer surface of the first outer ring gear 42 by moving with an electromagnetic force or the like, so that the rotation of the first outer ring gear 42 is decelerated. Further, when the second ring gear electromagnetic brake 62 is energized, the brake pad of the second ring gear electromagnetic brake 62 is moved by the electromagnetic force, and is brought into pressure contact with the outer surface of the second outer ring gear 52 so as to be in the second outer side. The rotation of the ring gear 52 is configured to decelerate.

  In the camshaft phase continuously variable drive device 1 ′ having the mysterious planetary gear mechanism 31, 32 having such a configuration, the crankshaft of the internal combustion engine is in a normal state where none of the electromagnetic brakes 16, 17, 61, 62 is operating. Is rotated, the cam shaft drive gear 4, the connecting shaft 3, the cam shaft 5, the bevel gears 11 'and 12', the bevel pinions 13, and the mysterious planetary gear mechanisms 31 and 32 are clockwise (indicated by arrows in FIG. 2). Direction). When the control device operates only the first ring gear electromagnetic brake 61 by energization in this co-rotation state, the first outer ring gear 42 of the first mysterious planetary gear mechanism 31 receives the braking force from the first ring gear electromagnetic brake 61. Accordingly, the rotation of the first outer ring gear 42 decelerates more than the cam shaft 5 and the cam shaft drive gear 4, and the first bevel gear 11 ′ moves more slowly than the cam shaft drive gear 4 and moves the connecting shaft 3. Let

  More specifically, the first outer ring gear 42 in a decelerated state rotates (rotates and revolves) the first planetary gear 43, whereby rotation of the first inner ring gear 41 and the first bevel gear 11 ′ is caused by rotation of the connecting shaft 3. Is also moved to a slower state. At this time, based on the setting of the braking force of the first ring gear electromagnetic brake 61 and the setting of the reduction ratio of the first mysterious planetary gear mechanism 31, the rotation of the first bevel gear 11 ′ is caused by the camshaft 5 and the camshaft drive gear 4. Is set so as to decelerate more slowly than the operation of the first bevel gear electromagnetic brake 16. When the rotation of the first bevel gear 11 ′ is decelerated with such setting, the rotation of the bevel pinion 13, the differential of the pair of bevel gears 11 ′ and 12 ′, the camshaft drive gear of the connecting shaft 3, as in the first embodiment. Movement to the fourth side (left side in FIG. 2) is performed, and the camshaft 5 is shifted to a retarded state more slowly (in other words, at a slower speed) than when the first bevel gear electromagnetic brake 16 is operated. When the rotational phase detection sensor detects that the camshaft 5 has reached the target retardation rotational phase, the control device applies the first ring gear electromagnetic brake 61 to the first ring gear electromagnetic brake 61 based on the signal from the rotational phase detection sensor. The energization is cut off, the braking operation to the first outer ring gear 42 is released, and the camshaft drive gear 4, the connecting shaft 3, the camshaft 5, the bevel gears 11 'and 12', the bevel pinions 13 and the non-operating state. The mysterious planetary gear mechanisms 31 and 32 rotate together in the retarded state.

  On the other hand, when the control device operates only the second ring gear electromagnetic brake 62 by energization in the above-mentioned co-rotation state, the second outer ring gear 52 of the second mysterious planetary gear mechanism 32 moves from the second ring gear electromagnetic brake 62. Upon receiving the braking force, the rotation of the second outer ring gear 52 is decelerated more than the cam shaft 5 and the cam shaft drive gear 4, and the second bevel gear 12 ′ is further decelerated than the cam shaft drive gear 4 and the connecting shaft 3. Move.

  Specifically, the second outer ring gear 52 in the decelerated state rotates (rotates and revolves) the second planetary gear 53, whereby the rotation of the second inner ring gear 51 and the second bevel gear 12 ′ is caused by the rotation of the connecting shaft 3. Is also moved to a slower state. At this time, based on the setting of the braking force of the second ring gear electromagnetic brake 62 and the setting of the reduction ratio of the second mysterious planetary gear mechanism 32, the rotation of the second bevel gear 12 'is caused by the camshaft 5 and the camshaft drive gear 4 being rotated. Is set so as to decelerate more slowly than when the second bevel gear electromagnetic brake 17 is operated. When the rotation of the second bevel gear 12 'decelerates in such a setting, as in the first embodiment, the rotation of the bevel pinion 13 and the differential of the pair of bevel gears 11' and 12 ', the camshaft 5 side of the connecting shaft 3 The camshaft 5 is moved to the advanced angle state more slowly (in other words, at a slower speed) than when the second bevel gear electromagnetic brake 17 is operated. When the rotation phase detection sensor detects that the camshaft 5 has reached the target advance rotation phase, the control device applies the second ring gear electromagnetic brake 62 to the second ring gear electromagnetic brake 62 based on the signal from the rotation phase detection sensor. The energization is cut off, the braking operation to the second outer ring gear 52 is released, and the camshaft drive gear 4, the connecting shaft 3, the camshaft 5, the bevel gears 11 ′ and 12 ′, the bevel pinions 13, and the non-operating state The mysterious planetary gear mechanisms 31 and 32 rotate together in the above-mentioned advanced state.

  If the rotational phase of the camshaft 5 is changed by the operation of the mysterious planetary gear mechanisms 31 and 32 in this way, fine adjustment that is difficult with deceleration by the bevel gear electromagnetic brakes 16 and 17 can be executed. Therefore, it is possible to improve accuracy in changing the rotational phase of the camshaft 5. For example, if the number of teeth of the inner ring gears 41 and 51 is Zs = 65 and the number of teeth of the outer ring gears 42 and 52, which are standard gears, is Zn = 62, the reduction ratio i of the mysterious planetary gear mechanisms 31 and 32 is I = Zs / (Zn-Zs) = 65 / (62-65) =-21.66. Assuming that the rotating camshaft rotates at 2500 rpm before the ring gear electromagnetic brakes 61 and 62 are operated, when the ring gear electromagnetic brakes 61 and 62 are operated, the inner ring gears 41 and 51 and the inner ring gears are operated. The bevel gears 11 'and 12' connected to the gears 41 and 51 can be decelerated by 2500 / 21.66 = 115.4 rpm. If the strange planetary gear mechanisms 31 and 32 are used, it is possible to prevent the bevel gears 11 'and 12' from inadvertently shifting the rotation phase when the ring gear electromagnetic brakes 61 and 62 are not operating. In other words, the mysterious planetary gear mechanisms 31 and 32 can function as a locking mechanism for the bevel gears 11 'and 12'. Since the bevel gears 11 'and 12' themselves are also differential devices, they essentially have a lock structure that does not move with force from the reverse direction.

  Further, since the electromagnetic brake (ring gear electromagnetic brakes 61 and 62) is employed as the ring gear brake means, the ring gear brake means can be realized with a simple configuration. Furthermore, the time delay from the energization of the ring gear electromagnetic brakes 61, 62 to the start of braking of the ring gears 42, 52, and the time delay until the start of braking of the bevel gears 11 ', 12' can be shortened. Therefore, when energized, the ring gears 42 and 52 can be decelerated and the bevel gears 11 'and 12' can be decelerated without any delay.

  In the cam shaft phase continuously variable drive device 1 ′ of the second embodiment, the operation of the bevel gear electromagnetic brakes 16, 17 is executed to shift the phase of the rotating bevel gears 11 ′, 12 ′, thereby By performing the rough phase determining operation for changing the rotational phase of the shaft 5 and the operation of the ring gear electromagnetic brakes 61 and 62 after the rough phase determining operation to shift the phases of the rotating bevel gears 11 'and 12'. The cam shaft 5 can be changed to the target rotation phase by executing a fine phase determination operation for changing the rotation phase of the cam shaft 5 at a speed slower than the coarse phase determination operation. At this time, when the camshaft 5 is set in the retarded state before the change is executed, control for operating the first bevel gear electromagnetic brake 16 and the first ring gear electromagnetic brake 61 is executed by the control device. When the angular state is set, the control device executes control for operating the second bevel gear electromagnetic brake 17 and the second ring gear electromagnetic brake 62.

  More specifically, as shown in FIG. 4, at the start of execution of the change of the rotational phase, the control device performs control to execute the coarse phase determining operation to perform the bevel gear electromagnetic brake (the first bevel gear electromagnetic brake 16 or the second The bevel gear electromagnetic brake 17) is energized to change the rotational phase of the cam shaft 5. Then, the control device determines the progress of the change of the rotation phase of the camshaft 5 based on the signal from the phase shift detection sensor, and a predetermined value Δθ1 (for example, change) before the rotation phase of the camshaft 5 reaches the change target. When the value Δθ1 corresponding to 10% of the phase difference to the target before the start of execution is reached, the control device performs control to end the rough phasing operation, and the bevel gear electromagnetic brake (first bevel gear electromagnetic brake) 16 or the second bevel gear electromagnetic brake 17). Further, the control for executing the precise phase determination operation is performed to energize the ring gear electromagnetic brake (the first ring gear electromagnetic brake 61 or the second ring gear electromagnetic brake 62) to change the rotational phase of the cam shaft 5. Continue to do. At this time, the rotation of the bevel gears 11 ′ and 12 ′ receiving the braking force via the mysterious planetary gear mechanisms 31 and 32 is decelerated more slowly than in the rough phasing operation. Then, the control device determines the progress of the change of the rotation phase of the camshaft 5 based on the signal from the rotation phase detection sensor, and when the rotation phase of the camshaft 5 reaches the change target, the control device determines the precise phase. The control to end the operation is performed to cut off the energization to the ring gear electromagnetic brake (the first ring gear electromagnetic brake 61 or the second ring gear electromagnetic brake 62).

  If the rotational phase of the cam shaft 5 is changed by executing the coarse phase determination operation and the fine phase determination operation in this manner, the rotational phase of the cam shaft 5 can be changed quickly and accurately. In the coarse phasing operation and the subsequent precise phasing operation, the gears constituting the bevel gears 11 'and 12' and the wonder planetary gear mechanisms 31 and 32 are rotated only in a certain direction (pushing hand) to cam. In order to change the rotational phase of the shaft 5, errors in the rotational phase of the cam shaft 5 and noise (gears) caused by backlash of the screw structure of the bevel gears 11 ′ and 12 ′ moving on the connecting shaft 3 and the gear structure backlash. Noise due to collision between each other is difficult to occur. Further, since the mysterious planetary gear mechanisms 31, 32 are housed in the gear mechanism arrangement space portions 33, 37 formed in the bevel gears 11 ', 12', the camshaft phase continuously variable drive device 1 'can be easily made compact.

  In the camshaft phase continuously variable drive device 1 ′ in the second embodiment, the operation of changing the rotational phase performed using the mysterious planetary gear mechanisms 31 and 32 is executed as the device start operation before the rough phase determining operation. May be. For example, a pair of bevel gears 11 ′ and 12 ′ can be caused to act on the frictional force of the differential gear portion 2 (specifically, the static force generated between the connecting shaft 3 and the bevel pinion 13 only by the braking force by the electromagnetic brakes 16 and 17 for the bevel gear). It is difficult to start the differential smoothly against the frictional force) and the moment of inertia. However, if the braking force is transmitted from the ring gear electromagnetic brakes 61 and 62 via the mysterious planetary gear mechanisms 31 and 32, the difference is smooth. When it is easy to start the movement, it is preferable to execute the device starting operation by the mysterious planetary gear mechanisms 31 and 32 before the rough phasing operation. In short, if the torque capable of smoothly starting the differential can be applied to the bevel gears 11 ′ and 12 ′, only the bevel gear electromagnetic brakes 16 and 17 or the ring gear electromagnetic brakes 61 and 62 are used. 11 'and 12' may be started, or the first bevel gear electromagnetic brake 16 and the first ring gear electromagnetic brake 61 may be used together, or the second bevel gear electromagnetic brake 17 and the second ring may be used together. The differential of the bevel gears 11 ′ and 12 ′ may be started by using the gear electromagnetic brake 62 together.

  Further, although the fine phasing operation is continuously performed after the rough phasing operation, the present invention is not limited to this. For example, an interval may be provided between the coarse phasing operation and the fine phasing operation.

  By the way, in each said embodiment, although the right male screw 23 and the left male screw 24 were overlapped and formed only in the location which can be located between bevel gears 11 and 12 among the outer periphery of the connection shaft 3, this invention was formed. Is not limited to this. For example, the right male screw 23 and the left male screw 24 may be overlapped between the gear-side helical spline protrusion 21 and the camshaft-side helical spline protrusion 22 in the outer periphery of the connecting shaft 3. In short, the right male screw 23 and the left male screw 24 may be formed overlapping each other at least at a position that can be positioned between the bevel gears 11 and 12.

  Moreover, in each said embodiment, although the right internal thread 11b was formed in the 1st bevel gear 11, and the left internal thread 12b was formed in the 2nd bevel gear 12, this invention is not limited to this. In short, a right female screw may be formed in the central circular hole of one bevel gear, and a left female screw may be formed in the other bevel gear. For example, a left female screw is formed in the first bevel gear 11 and the second bevel gear 12 is formed. A right female thread may be formed.

  Further, in each of the above embodiments, the connection shaft 3 and the cam shaft drive gear 4 and the connection shaft 3 and the cam shaft 5 are connected by helical spline coupling, respectively, but the present invention is not limited to this. The point is that the camshaft drive gear and the camshaft are connected via the connecting shaft, and the rotational phase of the camshaft can be changed by the movement of the connecting shaft. For example, the connection between the connecting shaft and the camshaft drive gear Alternatively, one of the coupling shaft and the cam shaft may be a helical spline coupling, and the other may be a normal spline coupling (a spline coupling in which protrusions and grooves extend along the axial direction of the coupling shaft). However, if the camshaft drive gear, the coupling shaft, and the camshaft are coupled by two different helical spline couplings as in the above embodiments, the same coupling is achieved as compared with the case of coupling by a single helical spline coupling. Even with the amount of movement of the shaft, the change in the rotational phase of the camshaft increases. Therefore, it is preferable to easily change the rotation phase of the camshaft in a short time.

  In each of the above embodiments, the camshaft drive gear 4 is illustrated as an example of the transmission vehicle in the present invention, but the present invention is not limited to this. For example, a stepped pulley that receives a rotational force from a crankshaft of an internal combustion engine via a timing belt (stepped belt) may be adopted as a transmission vehicle. In short, any configuration may be used as long as it is a transmission vehicle that receives rotational force from the crankshaft side. In addition, the rotation direction and the movement direction of each component in the present invention are not limited to the settings exemplified in the above embodiments. In short, if the connecting shaft moves by shifting the phase between the bevel gears, and the change of the rotational phase of the cam shaft can be realized based on this movement, how to set the rotation direction and movement direction of each component May be.

  Further, in each of the above embodiments, the progress of the change of the rotational phase of the camshaft 5 due to the operation of the bevel gear electromagnetic brakes 16 and 17 is grasped by detecting the rotational phase shift of the first bevel gear 11 by the phase shift detection sensor, Although the progress of the change of the rotational phase of the cam shaft 5 due to the operation of the ring gear electromagnetic brakes 61 and 62 has been grasped by the detection of the rotational phase of the cam shaft 5 by the rotational phase detection sensor, the present invention is not limited to this. In short, if the control of the operation of the bevel gear brake means or the ring gear brake means can be executed in accordance with the progress of the change of the camshaft rotation phase, the progress of the change of the camshaft rotation phase by any means is possible. You may know.

  Further, as an example of the bevel gear brake means and the ring gear brake means in the present invention, a friction type electromagnetic brake that is directly pressed against an object to which a braking force is applied has been described, but the present invention is not limited thereto. For example, a non-contact type electromagnetic brake that generates a magnetic field by energization and applies a braking force by a resistance that crosses the magnetic field may be employed for the bevel gear brake means and the ring gear brake means in the present invention. Or you may employ | adopt not only utilization of electromagnetic force but mechanical brake means and hydraulic brake means like a toggle structure.

  The above-described embodiment should be considered as illustrative in all points and not restrictive. The present invention is not limited to the above description, but is defined by the scope of the claims, and includes all modifications within the scope and meaning equivalent to the scope of the claims.

DESCRIPTION OF SYMBOLS 1,1 'Cam shaft phase continuous variable drive device 2,2' Differential gear part 3 Connection shaft 4 Cam shaft drive gear 4a Helical spline groove 5 Cam shaft 5a Cam 5b Helical spline groove 10 Gear case 11, 11 '1st bevel gear 11a central circular hole 11b right female screw 12, 12 'second bevel gear 12a central circular hole 12b left female screw 13 bevel pinion 14a, 14b bearing 15 pinion support 16 first bevel gear electromagnetic brake 17 second bevel gear electromagnetic brake 21 gear side helical Spline ridge 22 Cam shaft side helical spline ridge 23 Right male screw 24 Left male screw 31 First wonder planetary gear mechanism 32 Second wonder planetary gear mechanism 33 First gear mechanism arrangement space portion 34 First shaft meshing portion 37 Second gear mechanism Arrangement space portion 38 Second shaft meshing portion 41 First inner ring gear 42 First outer ring gear 43 First planetary gear 44 First carrier 45 First sun gears 46, 47 First bearing 51 Second inner ring gear 52 Second outer ring gear 53 Second planetary gear 54 Second carrier 55 Second sun gear 56 57 Second bearing 61 Electromagnetic brake for first ring gear 62 Electromagnetic brake for second ring gear

Claims (5)

In the camshaft phase continuously variable drive device that rotates the camshaft by the rotational force received by the transmission vehicle from the crankshaft side of the internal combustion engine and changes the rotational phase of the camshaft,
A pair of bevel gears disposed between the transmission wheel and the camshaft and rotatably supported with the gear surfaces facing each other;
A connecting shaft that passes through a central circular hole established for each of the bevel gears, and connects the transmission wheel and the camshaft by helical spline coupling;
A bevel pinion meshed between opposing gear surfaces of the bevel gear;
A bevel gear brake means attached to each of the bevel gears to decelerate the rotation of the bevel gear;
With
A right female thread is formed in the central circular hole of one bevel gear, a left female thread is formed in the central circular hole of the other bevel gear,
On the outer periphery of the connecting shaft, a right male screw that is screwed to the right female screw of one bevel gear and a left male screw that is screwed to the left female screw of the other bevel gear are formed.
The cam shaft phase continuously variable drive device for an internal combustion engine, wherein the right male screw and the left male screw are overlapped and formed at a position that can be located at least between the bevel gears on the outer periphery of the connecting shaft.   The camshaft phase continuously variable drive device for an internal combustion engine according to claim 1, wherein the bevel gear brake means comprises an electromagnetic brake. Each of the bevel gears includes a wonder planetary gear mechanism configured by meshing a planetary gear with a pair of ring gears having different numbers of teeth,
The wonder planetary gear mechanism is characterized in that one of the pair of ring gears is connected to the bevel gear so as to rotate together, and the ring gear brake means is attached to the other ring gear. The camshaft phase continuously variable drive device for an internal combustion engine according to claim 2. A rough phasing operation for changing the rotational phase of the camshaft by shifting the phase of the rotating bevel gears by executing the operation of the brake means for the bevel gear;
After the coarse phasing operation, the ring gear brake means is operated to shift the phases of the rotating bevel gears, thereby changing the rotational phase of the camshaft at a slower speed than the coarse phasing operation. Operation and
The camshaft phase continuously variable drive device for an internal combustion engine according to claim 3, wherein:   5. The camshaft phase continuously variable drive device for an internal combustion engine according to claim 3 or 4, wherein the ring gear brake means comprises an electromagnetic brake.

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