JP2012145148A - Torque interrupting clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To secure dimensional accuracy with ease, and to increase responsiveness by reducing resistance generated by lubricating oil.SOLUTION: A torque interrupting clutch 81 is provided with protruding teeth 87, 89 mutually formed in the opposite surfaces of a relatively rotatable clutch cylinder 83 and a clutch ring 85 in a circumference direction with an predetermined interval to perform rotation, interlock, and interception between the clutch cylinder 83 and the clutch ring 85 through engagement with and disengagement from the protruding teeth 87, 89 by relatively moving in a rotating shaft center direction with respect to the clutch cylinder 83 to the clutch ring 85. An abutment part 137 of which the projection height in the rotating shaft center direction is lower than the protruding tooth 87 is arranged at the clutch cylinder 83 with a phase shifted in a rotating direction with respect to the protruding tooth 87, and the abutment part 137 is projected to the other protruding tooth 89 at an engagement protruding position of the corresponding protruding teeth 87, 89 of the clutch cylinder 83 and the clutch ring 85 to cause projection in the rotating shaft center direction of the clutch cylinder 83 and the clutch ring 85.

Description

  The present invention relates to a torque intermittent clutch used in a power transmission device of an automobile.

  As a conventional torque intermittent clutch, there is one described in Patent Document 1. This intermittent torque clutch includes a cylinder fixed to the rotating shaft and a sleeve that can slide on the rotating shaft, and the dog is alternately formed with dog teeth with low teeth and dog teeth with high teeth. ing. Dog teeth are formed on the sleeve. The dog teeth of the sleeve can mesh with the tooth gap between the dog teeth of the cylinder and transmit power from one to the other.

  In such a structure, the tip surface of the dog teeth of the sleeve meshes with the tooth gap between the dog teeth of the lower tooth and the dog teeth of the higher tooth of the cylinder.

  Therefore, the tooth tip surfaces of all the dog teeth of the sleeve abut against the tooth gap bottom of the cylindrical body.

  For this reason, it is necessary to obtain the dimensional accuracy of the tooth tip surfaces of all the dog teeth of the sleeve and the tooth gap bottom of the cylindrical body, and there is a problem that the cost increases.

  Also, since lubricating oil enters all the tooth grooves, when all the dog teeth on the sleeve mesh with the tooth grooves of the cylinder, the oil exclusion resistance increases, hindering the mesh meshing movement, and meshing. It was an obstacle to improving the entry (responsiveness) in the wrong direction.

  Furthermore, lubricating oil is interposed between all the tooth tip surfaces and the tooth bottom, and the viscosity resistance of the oil is added between all the tooth tip surfaces and the tooth bottom, resulting in an increase in the sleeve. This has hindered the movement of disengagement, and has been an obstacle to improving the detachability (responsiveness) in the disengagement direction.

JP-A-11-108239

  The problem to be solved is that it is necessary to obtain the dimensional accuracy between the tooth tip surface and the tooth gap bottom of all the dog teeth, and the cost is high, and the resistance due to the lubricating oil is an obstacle to improving the response. Is a point.

  The present invention makes it possible to improve the dimensional accuracy and to improve the response by reducing the resistance caused by the lubricating oil. Therefore, the teeth are formed at predetermined intervals in the circumferential direction between the opposed surfaces of a pair of relatively rotatable rotors. A torque intermittent clutch that engages and disengages the projecting teeth by relative movement of the rotating body in the direction of the rotation axis to interrupt rotation interlocking between the rotating bodies. The abutting portion having a height lower than the projecting tooth in the rotational axis direction and lower than the bottom of the tooth gap is provided, and the abutting portion is disposed at the engaging engagement position of the projecting teeth between the rotating bodies. Abutting on the projecting teeth is performed in the direction of the rotation axis between the rotating bodies.

  Since the present invention has the above-described configuration, the engagement / disengagement of the projecting teeth and the butting of the butting portion against the projecting teeth can be performed separately.

  For this reason, it becomes easy to obtain dimensional accuracy by reducing the number of abutting portions, and the cost can be reduced.

  Due to the reduction of the abutting locations and the formation of the clearance between the tooth tips, the exclusion resistance and viscosity resistance of the lubricating oil can be reduced, and the responsiveness in the meshing direction and the meshing separation direction can be improved.

It is a skeleton top view of a vehicle. Example 1 It is an expanded sectional view showing the front differential device periphery. Example 1 It is sectional drawing of a clutch cylinder. Example 1 It is sectional drawing of a clutch ring. Example 1 It is a front view which shows the protrusion tooth | gear of a clutch cylinder with a tooth gap. Example 1 It is a front view which shows the protrusion teeth of a clutch ring with a tooth gap. Example 1 It is a side view which shows detachment | leave and engagement of a clutch cylinder and a clutch ring. Example 1 It is a principal part side view which shows disengagement and engagement of a clutch cylinder and a clutch ring. Example 1 It is a principal part side view which shows disengagement and engagement of a clutch cylinder and a clutch ring. (Comparative example)

  The purpose of facilitating dimensional accuracy and improving the responsiveness by reducing the resistance caused by the lubricating oil is realized by the abutting portion separate from the engagement of the projecting teeth.

  FIG. 1 is a skeleton plan view of a four-wheel drive vehicle of a vertically mounted front engine / rear drive base (FR base) according to the first embodiment of the present invention, showing the arrangement of a torque transmission device.

  As shown in FIG. 1, the four-wheel drive vehicle 1 includes an engine 3, a motor / generator 4, a transmission 5, a transfer 7, a rear differential device 9, a front differential device 11, and an axle disconnect mechanism 13. .

  In the transfer 7, an output drive shaft 15 is coupled to an output side portion of the transmission 5, and a sprocket 17 is rotatably supported on the output drive shaft 15. A front-side intermittent mechanism 18 is provided between the sprocket 17 and the output drive shaft 15.

  That is, the sprocket 17 is integrally provided with a clutch gear 19. A clutch gear 21 is fixed to the output drive shaft 15, and the coupling between the clutch gears 19, 21 is interrupted by the movement of the coupling sleeve 23. The coupling sleeve 23 is driven by an electromagnetic actuator 25 such as a solenoid.

  A transmission shaft 27 is supported on the transfer 7 in parallel with the output drive shaft 15, and a sprocket 29 is fixed to the transmission shaft 27. A chain 31 is wound around the sprocket 29 and the sprocket 17.

  The output drive shaft 15 of the transfer 7 is coupled to the drive pinion shaft 35 via the propeller shaft 33, and the drive pinion gear 37 of the drive pinion shaft 35 is connected to the ring gear 39 of the rear differential device 9. Are engaged.

  Rear wheels 45 and 47 are linked to the rear differential device 9 via left and right axles 41 and 43.

  The transmission shaft 27 of the transfer 7 is coupled to the drive pinion shaft 51 side via a propeller shaft 49. The pinion gear 53 of the drive pinion shaft 51 is engaged with the ring gear 55 of the front differential device 11.

  A front wheel 59 is linked to the front differential device 11 via an axle 57 on one side, and a front wheel 63 is linked to the front differential device 11 via an axle 61 provided with an axle disconnect mechanism 13 on the other side. The axle 61 can be divided and connected by the axle disconnect mechanism 13.

  Therefore, torque is transmitted from the transmission 3 from the engine 3 or the engine 3 and the motor / generator 4 in a directly connected state via the output drive shaft 15. That is, torque can be transmitted to the rear differential device 9 via the output drive shaft 15, the propeller shaft 33, the drive pinion shaft 35, the drive pinion gear 37, and the ring gear 39.

  The rear differential device 9 can output the left and right rear wheels 45 and 47 via the left and right axles 41 and 43.

  On the other hand, when the clutch gears 19 and 21 are coupled by the coupling sleeve 23 and the axle disconnect / connect mechanism 13 is connected to the axle 57, the output drive shaft 15 to the sprocket 17, the chain 31, and the sprocket 29 Torque is transmitted to the front differential device 11 through the transmission shaft 27, the propeller shaft 49, the drive pinion shaft 51, the drive pinion gear 53, and the ring gear 55.

  The front differential device 11 can output to the left and right front wheels 59 and 63 via the left and right axles 57 and 61.

When the axle 57 is divided by the axle disconnect mechanism 13, torque transmission from the front differential device 11 to the left and right front wheels 59, 63 is not performed.
At this time, when the coupling sleeve 23 is moved by driving the electromagnetic actuator 25 and the coupling between the clutch gears 19 and 21 is cut off, the sprocket 17, the chain 31, and the sprocket 29 between the transfer 7 and the front differential device 11. Rotation of the transmission shaft 27, the propeller shaft 49, the drive pinion shaft 51, the drive pinion gear 53, the ring gear 55, etc. is stopped, and unnecessary driving can be avoided.

  Accordingly, two-wheel drive and four-wheel drive can be selectively performed by the intermittent control of the front-side intermittent mechanism 14 and the axle disconnect / connect mechanism 13.

  FIG. 2 is an enlarged cross-sectional view showing the periphery of the front differential device.

  As shown in FIG. 2, in the front differential device 11, the ring gear 55 is fixed to the outside of the differential case 65 by a bolt 57, and the pinion gears 69 and 71 are connected to the differential case 65 via a pinion shaft 67. It is supported rotatably. The left and right side gears 73 and 75 mesh with the pinion gears 69 and 71, and the intermediate shafts 77 and 79 on the side of the axles 57 and 61 are spline-fitted to both side gears 73 and 75.

  One intermediate shaft 79 is provided with an axle-disconnect mechanism 13, and this axle-disconnect mechanism 13 is a clutch as a pair of rotating bodies that can rotate relative to the torque intermittent clutch 81 of the embodiment of the present invention. A cylinder 83 and a clutch ring 85 are provided.

  The opposing surfaces of the clutch cylinder 83 and the clutch ring 85 are provided with protrusions 87 and 89 at predetermined intervals in the circumferential direction. The protrusions 87 and 89 are engaged and disengaged by relative movement of the clutch cylinder 83 and the clutch ring 85 in the direction of the rotation axis, and the rotation interlock between the clutch cylinder 83 and the clutch ring 85 is cut off.

  More specifically, the intermediate shaft 79 is divided into first and second shafts 91, 93, a clutch ring 85 is coupled to the first shaft 91, and a clutch cylinder 83 is coupled to the second shaft 93. Has been.

  FIG. 3 is a cross-sectional view of the clutch cylinder.

  As shown in FIG. 2 and FIG. 3, the clutch cylinder 83 is provided with a flange portion 97 on one side with an intermediate wall 95 in between and a cylinder portion 99 on the other side. The protruding teeth 87 are formed on the opposing surface of the flange portion 97. Bearing fitting portions 101 and 103 are formed on the inner peripheral side of the flange portion 97 and the outer peripheral portion adjacent to the flange portion 97, and a seal receiving portion 105 is formed on the outer peripheral portion adjacent to the bearing fitting portion 103. An inner spline 107 is formed on the inner periphery of the cylindrical portion 99.

  The clutch cylinder 83 is supported along the first shaft 91 by a bearing 109 fitted to the bearing fitting portion 101, and is rotatably supported by the housing 113 by a bearing 111 fitted to the bearing fitting portion 103. ing.

  The housing 113 is attached to the differential carrier 115.

  In the cylinder portion 99 of the clutch cylinder 83, the spline 117 of the second shaft 93 is spline-engaged with the inner spline 107, and the retaining ring 119 prevents the spline 117 from coming off.

  FIG. 4 is a sectional view of the clutch ring.

  As shown in FIGS. 2 and 4, the clutch ring 85 has the protruding teeth 89 formed on the opposing surface and a sliding engagement portion 121 protruding from the inner periphery.

  The slide engagement portion 121 is engaged with the slide engagement receiving portion 123 of the first shaft 91, is slidable in the axial direction, and is engaged in the circumferential direction.

  A wave spring 125 is interposed between the clutch cylinder 83 and the clutch ring 85, and the clutch ring 85 is urged in the meshing disengagement direction.

  The clutch ring 85 is supported by the electromagnetic actuator 127 so as to be movable in the direction of the axis of rotation, thereby causing the relative movement.

  The electromagnetic actuator 127 includes an electromagnet 129 supported on the differential carrier 115 side, and a magnetic ring 133 made of steel or the like supported on the first shaft 91 side via a stainless steel ring 131.

  When the electromagnet 129 is energized, the magnetic ring 133 moves to the clutch ring 85 side by a magnetic flux loop formed on the differential carrier 115 side around the electromagnet 129, and the clutch ring 85 is moved by the protrusion 131 a of the stainless steel ring 131. It moves in the direction of the clutch cylinder 83 against the urging force of the wave spring 125.

The two-wheel drive and the four-wheel drive can be performed by engaging and disengaging the clutch cylinder 83 and the clutch ring 85 by such an operation.
[Abutting part]
5 is a front view showing the teeth of the clutch cylinder together with the tooth groove, FIG. 6 is a front view showing the teeth of the clutch ring together with the tooth groove, and FIG. 7 is the disengagement and engagement of the clutch cylinder and the clutch ring. FIG.

  As shown in FIGS. 5 and 7, a projecting abutting portion 137 that protrudes lower than the other projecting teeth 87 on the clutch cylinder 83 that is one of the rotating bodies is formed on the projecting teeth 87. In contrast, the phase in the rotational direction is shifted.

  That is, two adjacent teeth are cut out, and the abutting portion 137 is formed in the original tooth gap portion at the center. There are at least two teeth to be excised, and the abutting portion 137 can be formed by increasing the teeth to be excised.

  For this reason, the interval 139 between the abutting portion 137 and the protruding teeth 87 on both sides is wider than the tooth gap 141. A natural R 143 is formed on the bottom side of the interval 139, and a natural R 145 is formed in the tooth gap 141.

  The abutting portions 137 are set at three equal intervals in the circumferential direction. This abutting part 137 should just be set to at least 3 places, and can also increase a setting location according to a transmission torque. The abutting portion 137 can also be formed on the clutch ring 85 side.

  The tips of the protruding teeth 87 and the abutting portions 137 are formed flat.

  As shown in FIGS. 6 and 7, the projecting teeth 89 of the clutch ring 85 are formed at regular intervals so as to mesh with the mating projecting teeth 87. A natural R149 is formed in the tooth gap 147.

The tip of the projecting tooth 89 is also formed flat. Note that the abutting portion 137 may be provided at a position where the phase in the rotational direction is shifted with respect to the projecting tooth 87, so that the projecting tooth 87 is not formed in a projecting shape. It can also be formed as an entire surface.

  In addition, the abutting portion 137 can be formed by forming a tooth bottom of another tooth gap deeply in a conventional dog clutch, except for a part of the tooth groove of the same rotating body, without shifting the phase. It is also possible to use the shallow tooth bottom as the abutting portion.

  Then, as shown in the lower part of FIG. 7 (4WD), at the meshing engagement position of the projecting teeth 87 and 89 between the clutch cylinder 83 and the clutch ring 85, the abutting portion 137 is one of the tips of the other projecting tooth 89. The clutch cylinder 83 and the clutch ring 85 are abutted in the direction of the rotation axis.

  At this time, the protrusions 87 and 89 are engaged with each other in the rotational direction on the tooth side surface.

  Accordingly, when the electromagnet 129 is energized, the clutch ring 85 moves as described above and meshes with the clutch cylinder 83 as shown in the lower part of FIG. 7, and when the energization is released, the energizing force of the wave spring 125 causes the clutch ring 85 to engage. The movement of 85 is returned and disengages as shown in the upper part of FIG. 7 (2WD).

  Even when the clutch ring 85 meshes and moves relative to the clutch cylinder 83, the teeth 87 and 89 of the clutch cylinder 83 and the clutch ring 85 have the same tooth height, and the abutting portion 137. Since the height is lower than the tooth height of the protrusion 87, the abutting portion 137 and the like are not lost.

  Further, the clutch ring 85 has teeth 89 of uniform tooth length formed at equal intervals, so that any one of the teeth 89 abuts against the abutting portion 137 at any meshing position with respect to the clutch cylinder 83. Can do.

  FIG. 8 is a side view of a main part showing the disengagement and engagement of the clutch cylinder and the clutch ring according to the embodiment, and FIG. 9 is a main view showing disengagement and engagement of the clutch cylinder and the clutch ring according to the comparative example. FIG. The comparative example of FIG. 9 is a conventional dog clutch without the abutting portion 137.

  In FIG. 8 of the embodiment of the present invention, when the transition is made from 2WD to 4WD, both the projecting teeth 87 and 89 are engaged while the abutting portion 137 contacts one of the projecting teeth 89.

  For this reason, the abutting location between the clutch cylinder 83 and the clutch ring 85 can be reduced, and the location where dimensional accuracy is ensured can be reduced.

  In addition, the meshing height in the tooth height direction of the protrusions 87 and 89 is adjusted, and gaps are formed by natural R149 and 143 between the protrusions 87 and 89 and the tooth grooves 149 and 141. For this reason, the lubricating oil can be easily removed from the tooth grooves 149 and 141, and it is possible to make it difficult to receive viscous resistance due to the lubricating oil between the tooth tip and the bottom of the tooth groove at the time of disconnection.

  On the other hand, in the conventional dog clutch shown in FIG. 9, the protruding teeth 87A and 89A are all engaged, and the flat tooth tips of the protruding teeth 87A abut against the flat bottom of the tooth groove 147A between the protruding teeth 89A.

For this reason, it is difficult for the lubricating oil in the tooth grooves 141A and 147A to be excluded when the protruding teeth 87A and 89A are engaged, and the viscous resistance due to the lubricating oil between the tooth tips of the protruding teeth 87A and the bottom of the tooth groove 147A at the time of disengagement. It becomes easy to receive.
[Effect of Example]
In the embodiment of the present invention, the clutch cylinder 83 and the clutch cylinder 83 of the clutch ring 85 are provided with projecting teeth 87 and 89 formed at predetermined intervals in the circumferential direction between the opposed surfaces of the clutch cylinder 83 and the clutch ring 85 that are relatively rotatable. Is a torque intermittent clutch 81 that engages and disengages the projecting teeth 87 and 89 by relative movement in the direction of the rotation axis with respect to the clutch cylinder 83 and the clutch ring 85, and rotates the clutch cylinder 83. An abutting portion 137 having a projecting height in the axial direction lower than that of the projecting teeth 87 is provided with a phase shift in the rotational direction with respect to the projecting teeth 87, and the engagement of the projecting teeth 87 and 89 between the clutch cylinder 83 and the clutch ring 85. At the mating position, the abutting portion 137 is abutted against the other projecting tooth 89 so that the abutting in the direction of the rotation axis between the clutch cylinder 83 and the clutch ring 85 is performed.

  For this reason, the abutting part of the abutting part 137 and the projecting tooth 89 is reduced, and it becomes easy to obtain dimensional accuracy, and the cost can be reduced.

  Since the mesh height of the teeth 87 and 89 in the tooth height direction is adjusted, and gaps are formed by natural R149 and 143 between the teeth 87 and 89 and the tooth grooves 149 and 141, the exclusion resistance of the lubricating oil, The viscous resistance can be reduced, and the responsiveness in the meshing direction and the meshing separation direction can be improved.

  The abutting portions 137 were set at least at three locations in the circumferential direction.

  For this reason, the abutting of the abutting portion 137 can be stabilized, and rattling between the clutch cylinder 83 and the clutch ring 85 can be suppressed.

  The abutting portion 137 was formed by cutting out at least two projecting teeth adjacent in the circumferential direction on the facing surface of the clutch cylinder 83.

  For this reason, the meshing strength can be maintained without the protrusions 87 being unnecessarily reduced.

The clutch cylinder 83 and the clutch ring 85 are provided in the axle disconnect / connect mechanism 13 that performs torque division / connection on the axle 61.

  For this reason, it is possible to reduce the cost of the axle-disconnect mechanism 13 and improve the responsiveness in the meshing direction and the meshing disengagement direction.

  In the axle disconnect device 13, the clutch ring 85 and the clutch cylinder 83 are coupled to the first and second shafts 91 and 93 on the axle 61 side, respectively, and the clutch ring 85 drives the electromagnetic actuator 127. By this, it is supported so as to be movable in the direction of the axis of rotation, and relative movement is performed.

  For this reason, the response of the electromagnetic actuator 127 can be improved by reducing the exclusion resistance and viscosity resistance of the lubricating oil.

13 Axle-disconnect mechanism 81 Torque intermittent clutch 83 Clutch cylinder 85 Clutch ring 87, 89 Projection tooth 91 First shaft 93 Second shaft 127 Electromagnetic actuator 137 Contact portion

Claims (6)

Protruding teeth formed at predetermined intervals in the circumferential direction between the opposed surfaces of a pair of rotating bodies capable of relative rotation,
A torque intermittent clutch that engages and disengages the protruding teeth by relative movement in the direction of the rotation axis of the rotating body to perform rotation interlocking between the rotating bodies;
One of the rotating bodies is provided with an abutting portion whose height in the rotation axis direction is lower than the protruding teeth of the same rotating body and higher than the bottom of the tooth gap,
At the meshing engagement position of the projecting teeth between the rotating bodies, the butting portion is abutted against the projecting teeth of the other rotating body to cause the butting in the direction of the rotation axis between the rotating bodies.
Torque intermittent clutch characterized by that. The torque intermittent clutch according to claim 1,
The abutting portion is formed in a projecting shape and provided at a position shifted in the rotational direction phase with respect to the projecting teeth of the same rotating body,
Torque intermittent clutch characterized by that. The torque intermittent clutch according to claim 1 or 2,
The abutting portions are set at least at three locations in the circumferential direction.
Torque intermittent clutch characterized by that. The torque intermittent clutch according to any one of claims 1 to 3,
The abutting portion is formed by cutting out at least two projecting teeth adjacent in the circumferential direction on one facing surface of the rotating body,
Torque intermittent clutch characterized by that. The torque intermittent clutch according to any one of claims 1 to 4,
The pair of rotating bodies is provided in an axle disconnect / connect mechanism that performs torque division / connection on an axle.
Torque intermittent clutch characterized by that. The torque intermittent clutch according to claim 5,
The axle disconnect device is connected to the first and second shafts on the axle side, and the rotating body is supported so that one of the rotating bodies can move in the direction of the rotation axis by driving an electromagnetic actuator. The relative movement is performed,
Torque intermittent clutch characterized by that.

Images