JP6260367B2 - Clutch device - Google Patents

Description

  The present invention relates to a clutch device that removably connects members.

  Conventionally, for example, an electromagnetic clutch described in Patent Document 1 is known as a clutch device that connects a pair of members in a vehicle.

  The electromagnetic clutch described in Patent Document 1 includes an electromagnetic actuator and a pair of dog teeth meshed with each other. Of the pair of dog teeth, one dog tooth is supported so that it cannot rotate relative to the case fixed to the vehicle body and can move in the axial direction, and the other dog tooth is fixed to the rotating member (sun gear of the planetary gear mechanism). ing. Each dog tooth is formed with a plurality of meshing teeth for meshing. When one dog tooth meshes with the other dog tooth, the rotating member is connected to the other dog tooth as the fixing portion via the one dog tooth, and the rotation is restricted.

  The electromagnetic actuator includes an electromagnetic coil that generates a magnetic force by a current supplied from a control device, a yoke that holds the electromagnetic coil, a plunger that moves in an axial direction by the magnetic force of the electromagnetic coil, and a return that returns the plunger to its original position. And a spring. When the electromagnetic coil is energized, the plunger moves so that one dog tooth meshes with the other dog tooth. When the energization of the electromagnetic coil is interrupted, the plunger returns to the original position by the spring force of the return spring, and the engagement of the pair of dog teeth is released. In the holding state in which the engagement of the pair of dog teeth is maintained, a current having a holding current value smaller than the current value when the plunger is moved is supplied to the electromagnetic coil.

  The control device for controlling the electromagnetic clutch described in Patent Document 1 has coil temperature estimation means for estimating the temperature of the electromagnetic coil, and the temperature of the electromagnetic coil estimated by the coil temperature estimation means is within a normal temperature range. When deviating, in order to protect the electromagnetic clutch from overheating, the current supply to the electromagnetic coil is cut off and the electromagnetic clutch is released.

JP 2009-210110 A

  In the electromagnetic clutch described in Patent Document 1, it is necessary to continue energization of the electromagnetic coil in order to maintain the meshing of the pair of dog teeth. For this reason, if the time for maintaining the meshing state of the pair of dog teeth is long, the power consumption in the electromagnetic coil is increased and the temperature of the electromagnetic coil is increased. As described above, in the electromagnetic clutch described in Patent Document 1, when the temperature of the electromagnetic coil deviates from the normal temperature range, the current supply from the control device is cut off, so that the engagement of the pair of dog teeth is maintained for a long time. May be difficult to do.

  Therefore, the present invention does not require energization of the electromagnetic coil when maintaining the connection between the members, can reduce power consumption, and can maintain the connected state for a long time. The purpose is to provide.

  In order to solve the above-mentioned problem, the present invention is a clutch device that releasably connects a first member and a second member, wherein the first member engages with the first member and the second member. A connecting position for connecting the first member and the second member; an annular connecting member that moves forward and backward in an axial direction between non-connecting positions that allow the first member and the second member to rotate relative to each other; and the connecting member A pressing member that presses the pressing member in the axial direction, and a rotational force applying mechanism that applies a rotational force that rotates the pressing member relative to the connecting member, and each of the connecting member and the pressing member includes: A cam mechanism comprising a cam portion provided on one member of the connecting member and the pressing member and a protrusion provided on the other member, wherein the connecting member is in the unconnected position. The tip of the projection abuts when A first recess, and a second recess formed at a position shifted in the axial direction with respect to the first recess, and a tip of the protrusion abuts when the connecting member is in the connecting position; By operating the rotational force applying mechanism, the connecting member and the pressing member are rotated relative to each other, and the tip of the protrusion slides on the cam surface formed between the first recess and the second recess. A clutch device is provided in which the connecting member moves forward and backward between the connecting position and the non-connecting position.

  According to the present invention, it is not necessary to energize the electromagnetic coil when maintaining the connection between the members, so that the power consumption can be reduced, and the connected state can be maintained for a long time.

1 is a schematic configuration diagram of a four-wheel drive vehicle equipped with a clutch device according to a first embodiment of the present invention. It is sectional drawing which shows the structural example of a clutch apparatus and its peripheral part. It is a principal part enlarged view of the clutch apparatus in FIG. It is explanatory drawing which illustrates the structure of a cam part typically, (a) is the expanded view which expand | deployed the cyclic | annular cam part on the plane, (b) is the B section enlarged view of (a). It is a principal part enlarged view of the clutch apparatus which concerns on the 2nd Embodiment of this invention. It is a principal part enlarged view of the clutch apparatus which concerns on 2nd Embodiment.

[First Embodiment]
Hereinafter, a clutch device according to a first embodiment of the present invention and a four-wheel drive vehicle including the clutch device will be described in detail with reference to the drawings.

(Overall configuration of a four-wheel drive vehicle)
FIG. 1 is a schematic configuration diagram of a four-wheel drive vehicle 1 on which a clutch device according to an embodiment of the present invention is mounted. The four-wheel drive vehicle 1 includes a driving force transmission system 10, an engine 11 as a drive source, a transmission 12, front wheels 13L and 13R as main drive wheels, and rear wheels 14L and 14R as auxiliary drive wheels. In FIG. 1, the letter “L” in the code is used to mean the left side with respect to the forward direction of the four-wheel drive vehicle 1, and the letter “R” means the right side with respect to the forward direction of the four-wheel drive vehicle 1.

  The driving force transmission system 10 is disposed together with the front differential 15 and the rear differential 16 on a driving force transmission path from the transmission 12 to the front wheels 13L and 13R and the rear wheels 14L and 14R in the four-wheel drive vehicle 1. The driving force transmission system 10 includes a propeller shaft 17 that transmits the driving force (torque) of the engine 11 from the front wheels 13L and 13R to the rear wheels 14L and 14R, and the upstream side of the driving force transmission path from the propeller shaft 17. The clutch device 2 is disposed at a position where the transmission of the driving force of the engine 11 can be cut off, and the torque coupling 3 is disposed between the rear differential 16 and the left rear wheel 14L. The clutch device 2 is accommodated in the transfer case 100 together with the front differential 15.

  The clutch device 2 and the torque coupling 3 are controlled by the control device 4. A first rotation sensor 41 that detects the rotation speed of the propeller shaft 17 and a second rotation sensor 42 that detects the rotation speed of the front differential case 150 of the front differential 15 are connected to the control device 4.

  The driving force of the engine 11 is always transmitted to the front wheels 13L and 13R via the transmission 12 and the front differential 15. The driving force of the engine 11 is transmitted to the rear wheels 14L and 14R via the transmission 12, the clutch device 2, the propeller shaft 17, the torque coupling 3, and the rear differential 16. The control device 4 controls the clutch device 2 and the torque coupling 3 based on, for example, a driving state such as a differential rotation speed between the front wheels 13L and 13R and the rear wheels 14L and 14R and an acceleration operation amount by an accelerator pedal by a driver. To do.

  The front differential 15 includes left and right side gears 151L and 151R, a pair of pinion gears 152, a pinion shaft 153 that rotatably supports the pair of pinion gears 152, and a front differential case 150 that supports the pinion shaft 153. The driving force output from the transmission 12 is directly transmitted to the front differential case 150 by the meshing of the gears.

  The side gear 151L is connected to the left front wheel 13L via a front wheel side axle shaft 154L. The side gear 151R is coupled to the right front wheel 13R via a front wheel side axle shaft 154R. The pair of pinion gears 152 mesh with the side gears 151L and 151R with their gear axes orthogonal to each other. Further, the front differential case 150 is formed with a cylindrical portion 150a extending along the axle shaft 154R.

  The rear differential 16 includes left and right side gears 161L and 161R, a pair of pinion gears 162, a pinion shaft 163 that rotatably supports the pair of pinion gears 162, and a rear differential case 160 that supports the pinion shaft 163. The side gear 161L is connected to the left rear wheel 14L via the torque coupling 3 and the axle shaft 163L on the rear wheel side. The side gear 161R is connected to the right rear wheel 14R via a rear wheel axle shaft 163R.

  A front wheel side bevel gear mechanism 18 including a drive pinion 181 and a ring gear 182 that are meshed with each other is disposed at the front wheel side end of the propeller shaft 17. The drive pinion 181 rotates integrally with the propeller shaft 17. Ring gear 182 receives the driving force of engine 11 through clutch device 2.

  A rear wheel side bevel gear mechanism 19 including a pinion gear 191 and a ring gear 192 that mesh with each other is disposed at the rear wheel side end of the propeller shaft 17. The pinion gear 191 rotates integrally with the propeller shaft 17. The ring gear 192 rotates integrally with the rear differential case 160 of the rear differential 16.

  The torque coupling 3 includes a bottomed cylindrical housing 30 connected to the side gear 161L of the rear differential 16 so as not to rotate relative thereto, an axial inner shaft 31 connected to the axle shaft 163L so as not to rotate relative thereto, and a housing 30. And the inner shaft 31, a multi-plate clutch 32, an electromagnetic coil 33 to which electric current is supplied from the control device 4, and a magnetic force of the electromagnetic coil 33, and the relative rotation between the housing 30 and the inner shaft 31. And a cam mechanism 34 that presses the multi-plate clutch 32. In the torque coupling 3, the cam mechanism 34 presses the multi-plate clutch 32 with a cam thrust according to the energization amount of the electromagnetic coil 33, and transmits a driving force between the housing 30 and the inner shaft 31.

  When the four-wheel drive vehicle 1 travels in a four-wheel drive state, the clutch device 2 and the torque coupling 3 are both in an operating state in which the drive force can be transmitted by the control of the control device 4, and the drive force of the engine 11 is It is transmitted from the front differential case 150 to the propeller shaft 17 via the device 2 and further transmitted from the propeller shaft 17 to the rear differential 16. The driving force transmitted to the rear differential 16 is distributed from the side gear 161L to the left rear wheel 14L via the torque coupling 3 and the axle shaft 163L, and from the side gear 161R to the right rear wheel 14R via the axle shaft 163R. Is done. The driving force transmitted to the axle shaft 163L via the torque coupling 3 changes according to the amount of current supplied from the control device 4 to the electromagnetic coil 33. A driving force corresponding to the driving force transmitted to the axle shaft 163L is also transmitted to the axle shaft 163R.

  On the other hand, when the vehicle travels in a two-wheel drive state in which the driving force is transmitted only to the front wheels 13L and 13R, both the clutch device 2 and the torque coupling 3 are in an inoperative state in which the transmission of the driving force is interrupted. At this time, the side gear 161R of the rear differential 16 rotates together with the rear wheel 14R as the vehicle travels. However, since the connection between the axle shaft 163L and the side gear 161L is interrupted by the torque coupling 3, the pair of pinion gears 162 idle. The rear differential case 160 does not rotate. That is, during traveling in the two-wheel drive state, the rotation of the propeller shaft 17 is stopped. As a result, the rotational resistance associated with the rotation of each part of the propeller shaft 17, the front wheel side bevel gear mechanism 18 and the rear wheel side bevel gear mechanism 19 is suppressed, and the running resistance is reduced. The fuel efficiency of the wheel drive vehicle 1 is improved.

  Further, when the control device 4 shifts the four-wheel drive vehicle 1 from the two-wheel drive state to the four-wheel drive state, the control device 4 first operates the torque coupling 3 to rotate the propeller shaft 17, and the first rotation sensor 41 and the first rotation sensor 41. When it is determined that the rotation of the clutch device 2 is synchronized based on the detection value of the two-rotation sensor 42, the clutch device 2 is operated. Hereinafter, the configuration of the clutch device 2 and its peripheral part will be described in more detail.

(Configuration of clutch device)
FIG. 2 is a cross-sectional view showing a configuration example of the clutch device 2 and its peripheral portion. FIG. 3 is an enlarged view of a main part of the clutch device 2 in FIG.

  The transfer case 100 includes a first case member 101 and a second case member 102. The first case member 101 and the second case member 102 are fixed to each other by unillustrated bolts. The clutch device 2 is accommodated over the first case member 101 and the second case member 102. Further, the second case member 102 has a lead-out port that leads out the axle shaft 154R, and the inner surface of the lead-out port and the axle shaft 154R are sealed by a seal member 290.

  The clutch device 2 removably connects the ring gear 182 of the bevel gear mechanism 18 on the front wheel side and the cylindrical input shaft member 20 that is connected to the cylindrical portion 150a of the front differential case 150 so as not to be relatively rotatable. Here, “engageable / disengageable” means that the connecting member 21 described later is engaged with the input shaft member 20 and the ring gear 182 together, and the input shaft member 20 and the ring gear 182 are connected so as to be able to transmit the driving force. This means that the connected state can be released by the movement of the member 21 and the input shaft member 20 and the ring gear 182 can be switched to a non-connected state in which the relative rotation is possible. The input shaft member 20 is an aspect of the first member of the present invention, and the ring gear 182 is an aspect of the second member of the present invention.

  The clutch device 2 is engaged at the input shaft member 20 and the ring gear 182 to connect the input shaft member 20 and the ring gear 182 and at a non-connecting position where the input shaft member 20 and the ring gear 182 can be rotated relative to each other. An annular connecting member 21 that moves forward and backward in the axial direction, an elastic member 22 that elastically biases the connecting member 21 along the axial direction, and a shaft that resists the biasing force of the elastic member 22. A pressing member 23 that presses in the direction and a rotational force applying mechanism 2 a that applies a rotational force that rotates the pressing member 23 relative to the connecting member 21 are provided.

  The rotational force imparting mechanism 2 a is an electromagnetic brake mechanism having an electromagnetic coil 24 that generates a magnetic force when energized, a yoke 25 that supports the electromagnetic coil 24, and an armature 26 that is attracted to the yoke 25 by the magnetic force of the electromagnetic coil 24. The rotational force applying mechanism 2 a is activated by energizing the electromagnetic coil 24, and the armature 26 and the yoke 25 come into contact with each other when the armature 26 is attracted to the yoke 25, and is generated on the contact surface between the armature 26 and the yoke 25. By applying a friction force to the pressing member 23, the pressing member 23 is rotated relative to the connecting member 21.

  In addition, each of the connecting member 21 and the pressing member 23 includes a cam mechanism including a cam portion provided on one member and a protrusion provided on the other member of the connecting member 21 and the pressing member 23. Configure. The cam portion and the protrusion are brought into contact with each other by the urging force of the elastic member 22. In the present embodiment, the connecting member 21 is provided with a cam portion 210, and the pressing member 23 is provided with a protrusion 231. By this cam mechanism, the connecting member 21 moves in the axial direction with respect to the pressing member 23.

  The input shaft member 20 has a cylindrical shape through which the axle shaft 154R on the front wheel side is inserted, and one end portion in the axial direction along the direction of the rotation axis O is spline-engaged with the cylindrical portion 150a of the front differential case 150. . Thereby, the input shaft member 20 is connected to the front differential case 150 so as not to be relatively rotatable. The input shaft member 20 is rotatably supported at one end on the front differential case 150 side by a first ball bearing 291 on the first case member 101 of the transfer case 100 and at the other end by a second ball bearing 292. The transfer case 100 is rotatably supported by the second case member 102. A spline engaging portion 201 that splines engages with the connecting member 21 is formed on the outer peripheral surface of a part of the input shaft member 20 in the axial direction so as to protrude outward.

  A cylindrical plunger 27 and a spacer 281 are disposed on the outer peripheral side of the input shaft member 20. The plunger 27 is disposed on the front differential case 150 side of the spline engaging portion 201 of the input shaft member 20, and the spacer 281 is disposed on the opposite side thereof. The plunger 27 integrally includes a cylindrical portion 270 and a flange portion 271 formed to project outward from one end portion of the cylindrical portion 270 on the front differential case 150 side.

  Between the flange portion 271 of the plunger 27 and the inward projection 101a formed on the first case member 101 of the transfer case 100, the elastic member 22 is disposed in a state compressed in the axial direction. In the present embodiment, the elastic member 22 is a coil spring. However, the elastic member 22 may be configured by, for example, arranging a plurality of disc springs in the axial direction, or may be configured by an elastic body such as rubber.

  Between the flange portion 271 of the plunger 27 and the elastic member 22, a needle thrust roller bearing 293 for facilitating the rotation of the plunger 27 is disposed. The elastic member 22 presses the connecting member 21 against the spline engaging portion 201 side of the input shaft member 20 via the needle-like thrust roller bearing 293 and the plunger 27. Further, when the connecting member 21 is engaged with the spline engaging portion 201, the other end portion of the cylindrical portion 270 of the plunger 27 (an end portion opposite to the elastic member 22 side) abuts against the spline engaging portion 201.

  An annular support member 282 that is coupled to the ring gear 182 so as not to be relatively rotatable and supports the ring gear 182 is disposed outside the cylindrical portion 270 of the plunger 27. The annular support member 282 is rotatably supported by the first case member 101 of the transfer case 100 via the first tapered roller bearing 294. The annular support member 282 is opposed to the axial end surface 21 a of the connecting member 21. The ring gear 182 is also supported by the second case member 102 of the transfer case 100 via the second tapered roller bearing 295.

  A spline engaging portion 183 that is spline engaged with the connecting member 21 is formed on the inner peripheral surface of the ring gear 182. A part of the spline engaging portion 183 faces the spline engaging portion 201 of the input shaft member 20 and is formed in a range longer than the spline engaging portion 201 of the input shaft member 20 in the axial direction.

  The yoke 25 is a magnetic body made of iron-based metal, and is fitted on the inner surface of the second case member 102 of the transfer case 100. The yoke 25 is formed with an annular recess 25 a for accommodating the electromagnetic coil 24. Further, the yoke 25 has an overhang portion 251 formed to protrude inward toward the input shaft member 20, and a needle thrust roller bearing 296 is disposed between the overhang portion 251 and the pressing member 23. Has been. The pressing member 23 is restricted from axial movement in a direction away from the connecting member 21 by the overhanging portion 251 of the yoke 25, and can be smoothly rotated with respect to the yoke 25 by the needle-like thrust roller bearing 296.

  As shown in FIG. 3, the pressing member 23 is disposed on the outer peripheral side of the cylindrical spacer 281, and has an annular base portion 230 and a plurality of protrusions 231 that protrude from the base portion 230 toward the connecting member 21 side. ing. In the base 230, holes 230a are formed at a plurality of locations in the circumferential direction (three locations in the present embodiment) at equal intervals. The protrusion 231 has a cylindrical shape, and the tip 231a has a hemispherical shape. The base end portion 231b of the protrusion 231 is fixed to the base portion 230, for example, by press fitting into the hole portion 230a. In addition, in this Embodiment, although the pressing member 23 is comprised by the combination of the base 230 and the some protrusion 231, you may comprise these as an integral member.

  The armature 26 is an annular plate-shaped magnetic body made of an iron-based metal, and is attracted to the yoke 25 by a magnetic force generated by a current supplied from the control device 4 to the electromagnetic coil 24. The control device 4 can adjust the current value of the current supplied to the electromagnetic coil 24 in a plurality of stages. The pressing member 23 is engaged with the armature 26 so as to be relatively movable in the axial direction and not to be relatively rotatable. More specifically, the armature 26 is provided with insertion holes 26a that are formed so as to penetrate in the axial direction at a plurality of locations (three locations in the present embodiment), and the protrusions 231 of the pressing member 23 are formed in the insertion holes 26a. Is inserted. With this configuration, the armature 26 can be moved along the rotation axis O while being guided by the protrusion 231.

  When the electromagnetic coil 24 is energized, one side surface of the armature 26 comes into contact with the end surface 25 b of the yoke 25, and a frictional force is generated between the armature 26 and the yoke 25. This frictional force is applied to the pressing member 23 at the protrusion 231 inserted through the insertion hole 26a. In other words, the pressing member 23 causes the plurality of protrusions 231 to pass through the plurality of insertion holes 26 a of the armature 26, respectively, so that a frictional force generated between the armature 26 and the yoke 25 is generated when the electromagnetic coil 24 is energized. receive. The pressing member 23 rotates relative to the connecting member 21 by this frictional force.

  That is, when the four-wheel drive vehicle 1 is traveling, the connecting member 21 rotates together with the ring gear 182, so that a frictional force generated between the yoke 25 fitted to the transfer case 100 and the armature 26 is applied to the pressing member 23. If it does, the press member 23 and the connection member 21 will rotate relatively. That is, the rotational force applying mechanism 2 a suppresses the rotation of the armature 26 by the frictional force generated between the armature 26 and the yoke 25, and the connecting member 21 and the pressing member 23 that rotate according to the rotation of the ring gear 182. Rotate relative with.

  As shown in FIG. 3, the connecting member 21 has a first spline engaging portion 211 that is spline engaged with the input shaft member 20 on the inner peripheral surface, and a second spline engaging portion that is spline engaged with the ring gear 182. 212 is provided on the outer peripheral surface. The first spline engaging portion 211 and the second spline engaging portion 212 are composed of a plurality of spline teeth extending in the axial direction parallel to the rotation axis O.

  When the connecting member 21 is in a connecting position for connecting the input shaft member 20 and the ring gear 182, the first spline engaging portion 211 is spline engaged with the spline engaging portion 201 of the input shaft member 20, and the second spline is connected. The engaging portion 212 is spline engaged with the spline engaging portion 183 of the ring gear 182. Further, when the connecting member 21 is in a non-connecting position where the input shaft member 20 and the ring gear 182 can be rotated relative to each other, the second spline engaging portion 212 is spline engaged with the spline engaging portion 183 of the ring gear 182. The first spline engaging portion 211 is not spline engaged with the spline engaging portion 201 of the input shaft member 20. That is, the connecting member 21 engages with the ring gear 182 at the connecting position and the non-connecting position, and engages with the input shaft member 20 only at the connecting position. FIG. 2 shows a state in which the connecting member 21 is in the connecting position above the rotation axis O, and shows a state in which the connecting member 21 is in the connecting position below the rotation axis O.

  In the connecting member 21, a cam portion 210 is formed at a central portion in the radial direction between the first spline engaging portion 211 and the second spline engaging portion 212. Further, the connecting member 21 has an inner flange portion 213 formed on the inner peripheral side of the cam portion 210, and an outer flange portion 214 formed on the outer peripheral side of the cam portion 210. The inner flange portion 213 and the outer flange portion 214 protrude toward the pressing member 23, and the protrusion 231 of the pressing member 23 contacts the cam portion 210 from between the inner flange portion 213 and the outer flange portion 214. Next, the configuration of the cam portion 210 will be described in detail.

  FIG. 4 is an explanatory diagram schematically illustrating the configuration of the cam unit 210. FIG. 4A shows a state in which the annular cam portion 210 is developed on a plane and viewed from a direction corresponding to the radial direction of the connecting member 21. FIG.4 (b) is the B section enlarged view of Fig.4 (a).

The cam portion 210 is formed at a position where the tip portion 231a of the protrusion 231 contacts when the connecting member 21 is in the non-connecting position, and a position offset in the axial direction with respect to the first recess 210a. And a second recess 210b with which the tip 231a of the projection 231 comes into contact when 21 is in the coupling position. In the present embodiment, the first recess 210a and the second recess 210b are respectively formed at three locations in the circumferential direction. The first concave portion 210a and the second concave portion 210b are recessed in the axial direction so that the bottom portions 210a ₁ and 210b ₁ face the axial end surface 21a.

  Between the 1st recessed part 210a and the 2nd recessed part 210b, the 1st thru | or 3rd cam surface 210c, 210d, 210e inclined with respect to the surface (virtual surface) orthogonal to the rotating shaft O is formed. . In the connecting member 21, the connecting member 21 and the pressing member 23 are rotated relative to each other by the operation of the rotational force applying mechanism 2a, and the tip portion 231a of the protrusion 231 is formed between the first recess 210a and the second recess 210b. By sliding on the first to third cam surfaces 210c, 210d, and 210e, it moves forward and backward between the connected position and the non-connected position.

The first recess 210a is located closer to the pressing member 23 (base 230 side) than the second recess 210b. Thereby, the axial thickness of the cam portion 210 is formed thicker in the first recess 210a than in the second recess 210b. When the bottom 210a ₁ of the first recess 210a to the axial distance between the bottom 210b ₁ of the second recess 210b to _{d 1,} connecting member 21, the relative rotation of the pressing member 23, the distance _{d 1} Reciprocate in range.

  4A and 4B, the protrusions 231 that are in contact with the first concave portion 210a and the second concave portion 210b are indicated by phantom lines (two-dot chain lines) for the sake of explanation. However, actually, when one projection 231 of the plurality of projections 231 contacts the first recess 210a, the other projection 231 also contacts the first recess 210a at the same time. When 231 contacts the second recess 210b, the other protrusions 231 also contact the second recess 210b at the same time. Further, when the four-wheel drive vehicle 1 moves forward, the relative movement direction of the pressing member 23 with respect to the connecting member 21 is an arrow A direction shown in FIG.

Cam portion 210 includes a bottom portion 210a ₁ circumferentially in the direction of arrow A cam angle theta ₁ of the first cam surface 210c extending toward the (relative rotational direction of the pressing member 23) of the coupling member 21 from the first recess 210a, the Unlike from the bottom 210b ₁ of the second recesses 210b and the cam angle theta ₂ in the circumferential direction to extend toward the direction of arrow a second cam surface 210d of the connecting member 21 with each other, the cam angle theta ₁ of the first cam surface 210c and the second greater than the cam angle theta ₂ of the cam surface 210d. That is, the cam portion 210 has a cam angle θ of the first cam surface 210c of the first recess 210a located on the opposite side of the first recess 210a and the second recess 210b from the pressing direction of the elastic member 21 by the pressing member 23. ₁ is greater than the cam angle theta ₂ of the second cam surface 210d of the second recess 210b located in the pressing direction.

The rotational force applying mechanism 2 a applies a rotational force according to the cam angle θ ₁ of the first cam surface 210 c or the cam angle θ ₂ of the second cam surface 210 d and the biasing force of the elastic member 22 to the pressing member 23. From the state projections 231 abuts against the bottom portion 210 b ₁ of the second recess 210 b, the pressing member 23 rotational force applying mechanism 2a is actuated to rotate relative to the connecting member 21 in the direction of the arrow A, the projection 231 tip 231a There slid second cam surface 210d, to contact the bottom portion 210a ₁ of the first recess 210a. Thereby, the connection member 21 moves from the connection position to the non-connection position.

Further, from the state tip 231a of the protrusion 231 abuts against the bottom portion 210a ₁ of the first recess 210a, the pressing member 23 rotational force applying mechanism 2a is actuated to rotate relative to the connecting member 21 in the arrow A direction, over the top 210f of the cam portion 210 tip 231a of the projection 231 slides the first cam surface 210c, contacts the bottom 210b ₁ of the second recess 210b slides the third cam surface 210e. Thereby, the connection member 21 moves from the non-connection position to the connection position.

In this embodiment, although the cam angle theta ₃ of the third cam surface 210e is formed larger than the cam angle theta ₂ of the cam angle theta ₁ and the second cam surface 210d of the first cam surface 210c, the 3 may be a cam angle theta ₃ of the cam surface 210e at the same angle as the cam angle theta ₂ of the second cam surface 210d. The cam angles θ _{1 to} θ ₃ are angles formed by the first to third cam surfaces 210c, 210d, and 210e with the circumferential direction of the connecting member 21, and in FIGS. 3A and 3B, the cam angles θ ₁ to θ ₃ is expressed as an angle (subordinate angle) formed between the first to third cam surfaces 210 c, 210 d, and 210 e and the axial end surface 21 a of the connecting member 21.

As described above, the cam angle theta ₁ of the first cam surface 210c is pressed when is greater than the cam angle theta ₂ of the second cam surface 210d, the projections 231 tip 231a slides on the first cam surface 210c The rotational resistance force received by the member 23 is greater than the rotational resistance force received by the pressing member 23 when the tip portion 231a of the protrusion 231 slides on the second cam surface 210d. That is, when the tip 231a of the protrusion 231 slides on the first cam surface 210c, a current larger than the minimum current required when the tip 231a of the protrusion 231 slides on the second cam surface 210d is applied. It is necessary to supply the electromagnetic coil 24.

Therefore, in the control device 4, the tip portion 231a of the protrusion 231 can slide on the second cam surface 210d, and the tip portion 231a of the protrusion 231 cannot slide on the first cam surface 210c. range current of the current value of by supplying to the electromagnetic coil 24, stop the relative rotation of the pressing member 23 and the connecting member 21 in a state in which the leading end portion 231a of projection 231 abuts the bottom portion 210a ₁ of the first recess 210a Can be made. That is, the control device 4 does not require position information from a sensor that can detect the position of the connecting member 21 in the axial direction, for example, and only by adjusting the current value of the current supplied to the electromagnetic coil 24. The member 21 can be moved from the connection position to the non-connection position.

Further, the control unit 4, the current of the current value capable of sliding the distal end portion 231a of the projections 231 is the first cam surface 210c, the leading end portion 231a of projection 231 to the bottom 210a ₁ of the first recess 210a equivalent By supplying the electromagnetic coil 24 from the contacted state to the electromagnetic coil 24 for a predetermined time required to get over the top 210f, the connecting member 21 can be moved from the non-connected position to the connected position. At this time, the tip portion 231a of the protrusion 231, coupling member 21 slides the third cam surface 210e by the force applied from the elastic member 22 abuts against the bottom portion 210 b ₁ of the second recess 210b.

Thus movement, the control device 4, when switching the connection state of the clutch device 2 and a non-connected state, the tip end portion 231a of the protrusion 231 from the bottom 210a ₁ of the first recess 210a to the bottom 210b ₁ of the second recess 210b during, or while moving from the bottom 210b ₁ of the second recess 210b to the bottom 210a ₁ of the first recess 210a, it may be energized to the electromagnetic coil 24, after the completion of the movement, to cut off the energization of the electromagnetic coil 24 However, the connected state or the unconnected state is maintained. That is, the connecting member 21, because it is biased in the pressing member 23 side by the elastic member 22, the distal end portion 231a of the projections 231 by the biasing force bottom 210b of the bottom portion 210a ₁ or the second recess 210b of the first recess 210a ₁ , the tip 231a of the protrusion 231 does not come out of the first recess 210a or the second recess 210b. Thereby, the control device 4 can stop the current supply to the electromagnetic coil 24 while the four-wheel drive vehicle 1 continues in the four-wheel drive state or the two-wheel drive state.

(Operation and effect of the first embodiment)
According to the first embodiment described above, the following operations and effects can be obtained.

(1) While the clutch device 2 is in the connected state (four-wheel drive state of the four-wheel drive vehicle 1) or the clutch device 2 is not connected (two-wheel drive state of the four-wheel drive vehicle 1), the control device 4 continues. Since the current supply to the electromagnetic coil 24 can be stopped, the power consumption for the operation of the clutch device 2 can be reduced, and the temperature rise of the electromagnetic coil 24 can be suppressed. . As a result, it is possible to maintain a connection state over a long time.

(2) Since the cam angle theta ₁ of the first cam surface 210c larger than the cam angle theta ₂ of the second cam surface 210d, by adjusting the current supplied from the control unit 4 to the electromagnetic coil 24, the tip of the projection 231 the relative rotation of the pressing member 23 and the connecting member 21 can be stopped in a state where part 231a is in contact with the bottom 210a ₁ of the first recess 210a. This facilitates control when shifting the clutch device 2 from the connected state to the non-connected state.

(3) Since the rotational force imparting mechanism 2a is composed of an electromagnetic brake mechanism, when the clutch device 2 shifts from the connected state to the non-connected state, and when the clutch device 2 shifts from the non-connected state to the connected state, it is promptly A rotational force for rotating the pressing member 23 relative to the connecting member 21 can be generated.

(4) Since the protrusion 231 is inserted through the insertion hole 26a formed in the armature 26, and the relative rotation between the pressing member 23 and the armature 26 is restricted thereby, the rotational force generated by the rotational force applying mechanism 2a is generated. While being able to give reliably to the press member 23, the structure of the clutch apparatus 2 is simplified and it can contribute also to size reduction of an apparatus.

(5) The connecting member 21 has a first spline engaging portion 211 that is spline engaged with the input shaft member 20 on the inner peripheral surface, and a second spline engaging portion 212 that is spline engaged with the ring gear 182 on the outer peripheral surface. Therefore, it is possible to easily switch between the connected state and the non-connected state of the clutch device 2 by moving the connecting member 21 in the axial direction.

[Second Embodiment]
Next, a clutch device 2A according to a second embodiment of the present invention will be described with reference to FIGS. FIG. 5 is a cross-sectional view showing a configuration example of the clutch device 2A according to the second embodiment and its peripheral portion. FIG. 6 is an enlarged view of a main part of the clutch device 2A according to the second embodiment.

  The clutch device 2A has the same function as the clutch device 2 according to the first embodiment, but the configuration of the connecting member 21A, the pressing member 23A, and the armature 26A is related to the first embodiment. This is different from the configuration of the connecting member 21, the pressing member 23, and the armature 26 of the clutch device 2. 5 and 6, members and the like that are the same as those described in the first embodiment are denoted by the same reference numerals, and redundant description thereof is omitted.

  In the first embodiment, the cam portion 210 is provided on the connecting member 21 and the protrusion 231 is provided on the pressing member 23. However, in the second embodiment, the protrusion 215 is provided on the connecting member 21A. A cam portion 230A is provided on the pressing member 23A. The protrusion 215 and the cam portion 230A constitute a cam mechanism that moves the connecting member 21A in the axial direction with respect to the pressing member 23A.

  The connecting member 21A has an annular base portion 210A and a plurality of columnar protrusions 215 that protrude from the base portion 210A toward the pressing member 23A. 210 A of base parts have the 1st spline engaging part 211 which carries out a spline engagement with the spline engaging part 201 of the input shaft member 20 on an internal peripheral surface similarly to the connection member 21 which concerns on 1st Embodiment, and A second spline engaging portion 212 that engages with the spline engaging portion 183 of the ring gear 182 is provided on the outer peripheral surface. The base 210A has holes 210g into which a plurality of protrusions 215 are fitted at equal intervals in a plurality of locations in the circumferential direction. The tip 215a of the protrusion 215 is hemispherical, and the base end 215b of the protrusion 215 is fixed to the base 210A by press-fitting into the hole 210g, for example.

  The pressing member 23 </ b> A is in contact with a needle-like thrust roller bearing 296 disposed between the overhanging portion 251 of the yoke 25 and is restricted from moving in the axial direction. A spline engaging portion 232 is formed on the outer peripheral surface of the pressing member 23A.

  The armature 26A has a spline engagement portion 261 that engages with the spline engagement portion 232 of the pressing member 23A on the inner peripheral portion thereof. The pressing member 23A is connected to the armature 26A so as not to rotate relative to the armature 26A by the spline engaging portion 232 engaging the spline engaging portion 261 of the armature 26A.

  The distal end portion 251a of the protrusion 215 of the connecting member 21A that receives the urging force of the elastic member 22 contacts the cam surface 230b of the cam portion 230A of the pressing member 23A. The thickness of the cam portion 230A in the axial direction of the pressing member 23A varies depending on the position in the circumferential direction. The cam surface 230b is formed in the same manner as the first to third cam surfaces 210c, 210d, and 210e of the cam portion 210 described with reference to FIG. 4 in the description of the first embodiment. When the pressing member 23A rotates relative to the connecting member 21A and the protrusion 215 of the connecting member 21A slides on the cam surface 230b, the connecting member 21A moves along the rotation axis O between the connected position and the non-connected position. To move in the axial direction. As a result, the connected state and the disconnected state of the clutch device 2A are switched.

  Also according to the present embodiment, it is possible to obtain the same operations and effects as the operations and effects described in the first embodiment.

  As mentioned above, although this invention was demonstrated based on 1st and 2nd embodiment, each embodiment described above does not limit the invention which concerns on a claim. In addition, the present invention can be appropriately modified and implemented without departing from the spirit thereof, and may be modified as shown below, for example.

  In the first embodiment, the case where the first recess 210a is positioned closer to the pressing member 23 than the second recess 210b has been described. On the contrary, the second recess 210b is more than the first recess 210a. May also be located on the pressing member 23 side. In this case, the spline engaging portion 201 of the input shaft member 20 is provided closer to the elastic member 22 than the position shown in FIG. 2, and when the connecting member 21 is separated from the pressing member 23 (base portion 230), the connecting member 21. The first spline engaging portion 211 is spline engaged with the spline engaging portion 201 of the input shaft member 20.

  In the first and second embodiments, when the connecting member 21 receives the pressing force from the pressing member 23 and moves in the axial direction, the connection between the input shaft member 20 and the ring gear 182 is released, and the connecting member 21 is Although the case where the input shaft member 20 and the ring gear 182 are connected by moving in the axial direction by the urging force of the elastic member 22 has been described, conversely, the connecting member 21 receives a pressing force from the pressing member 23. The input shaft member 20 and the ring gear 182 are connected by moving in the axial direction, and the connection between the input shaft member 20 and the ring gear 182 is released by moving the connecting member 21 in the axial direction by the biasing force of the elastic member 22. In this manner, the clutch devices 2 and 2A may be configured.

  In the first and second embodiments, the connection member 21 is engaged with the ring gear 182 at the connection position and the non-connection position, and the input shaft member 20 is engaged only at the connection position. Conversely, the clutch devices 2 and 2A may be configured such that the connecting member 21 engages with the input shaft member 20 at the connecting position and the non-connecting position, and engages with the ring gear 182 only at the connecting position. In this case, the connecting member 21 always rotates according to the rotation of the input shaft member 20.

  In the first and second embodiments, the input shaft member 20 as the first member of the present invention and the ring gear 182 as the second member of the present invention are both in the driving force transmission system 10 of the four-wheel drive vehicle 1. Although the case where it was a rotation member was demonstrated, not only this but the non-rotation member by which the 1st member or the 2nd member was connected with the vehicle body etc. may be sufficient. In this case, the clutch devices 2 and 2A function as a brake device that can stop the rotation of the rotating member.

  The clutch device 2 is not limited to being applied to the driving force transmission system 10 of the four-wheel drive vehicle 1, but can be applied to various mechanical devices such as machine tools.

DESCRIPTION OF SYMBOLS 1 ... Four-wheel drive vehicle, 2, 2A ... Clutch apparatus, 2a ... Torque-force provision mechanism, 3 ... Torque coupling, 4 ... Control apparatus, 10 ... Driving force transmission system, 11 ... Engine, 12 ... Transmission, 13L ... Left Front wheel, 13R ... right front wheel, 14L ... left rear wheel, 14R ... right rear wheel, 15 ... front differential, 16 ... rear differential, 17 ... propeller shaft, 18, 19 ... bevel gear mechanism, 20 ... input shaft member, 21, 21A: connecting member, 21a: axial end surface, 22: elastic member, 23, 23A ... pressing member, 24 ... electromagnetic coil, 25 ... yoke, 25a ... concave portion, 25b ... end surface, 26, 26A ... armature, 26a ... insertion hole 27 ... Plunger, 30 ... Housing, 31 ... Inner shaft, 32 ... Multi-plate clutch, 33 ... Electromagnetic coil, 34 ... Cam mechanism, 41 ... First Rotation sensor, 42 ... second rotation sensor, 100 ... transfer case, 101 ... first case member, 101a ... inward projection, 102 ... second case member, 150 ... front differential case, 150a ... cylindrical portion, 151L, 151R ... side gear , 152 ... Pinion gear, 153 ... Pinion shaft, 154L, 154R ... Axle shaft, 160 ... Rear differential case, 161L, 161R ... Side gear, 162 ... Pinion gear, 163 ... Pinion shaft, 163L, 163R ... Axle shaft, 181 ... Drive pinion, 182 ... Ring gear, 183 ... Spline engaging part, 191 ... Pinion gear, 192 ... Ring gear, 201 ... Spline engaging part, 210 ... Cam part, 210A ... Base, 210a ... First recess, 210a ₁ ... Bottom, 210b ... Second recess 2 10b ₁ ... bottom, 210c ... first cam surface, 210d ... second cam surface, 210e ... third cam surface, 210f ... top, 210g ... hole, 211 ... first spline engaging portion, 212 ... second spline engaging Joint part, 213 ... Inner collar part, 214 ... Outer collar part, 215 ... Projection, 215a ... Tip part, 215b ... Base end part, 230 ... Base part, 230A ... Cam part, 230a ... Hole part, 230b ... Cam surface, 231 ... Protrusions, 231a ... Front end part, 231b ... Base end part, 232 ... Spline engaging part, 251 ... Overhang part, 261 ... Spline engaging part, 270 ... Cylinder part, 271 ... Flange part, 281 ... Spacer, 282 Annular support member, 290 ... Seal member, 291 ... First ball bearing, 292 ... Second ball bearing, 293 ... Needle thrust roller bearing, 294 ... First tapered roller bearing, 295 ... Second tapered roller bearing 296 ... needle thrust roller bearings, A ... arrows, O ... Rotation axis, theta ₁ through? ₃ ... cam angle

Claims (7)

A clutch device for releasably connecting a first member and a second member,
A connection position that engages with the first member and the second member to connect the first member and the second member, and a non-connection position that allows the first member and the second member to rotate relative to each other. An annular connecting member that moves forward and backward in the axial direction,
A pressing member that presses the connecting member in the axial direction;
A rotational force applying mechanism for applying a rotational force for rotating the pressing member relative to the connecting member;
A part of each of the connecting member and the pressing member constitutes a cam mechanism including a cam portion provided on one member of the connecting member and the pressing member and a protrusion provided on the other member,
The cam portion is formed at a position where the distal end of the protrusion abuts when the connecting member is in the non-connecting position, and a position shifted in the axial direction with respect to the first recess. A second recess with which the tip of the protrusion abuts when the member is in the coupling position;
By operating the rotational force applying mechanism, the connecting member and the pressing member are rotated relative to each other, and the tip of the protrusion slides on the cam surface formed between the first recess and the second recess. The connecting member moves forward and backward between the connecting position and the non-connecting position;
Clutch device. The clutch device includes an elastic member that elastically urges the connecting member in the axial direction to contact the cam portion and the protrusion.
The pressing member presses the connecting member against the urging force of the elastic member, the cam angle of the first cam surface extending in the circumferential direction from the bottom of the first recess, and the periphery from the bottom of the second recess. The cam angles of the second cam surfaces extending in the direction are different from each other,
The rotational force applying mechanism applies a rotational force according to the cam angle of the first cam surface or the cam angle of the second cam surface and the biasing force to the pressing member.
The clutch device according to claim 1. The cam portion has a cam angle of a cam surface of a concave portion located on a side opposite to a pressing direction of the elastic member by the pressing member among the first concave portion and the second concave portion, and is located on the pressing direction side. Larger than the cam angle of the recess,
The clutch device according to claim 2. The rotational force applying mechanism includes an electromagnetic coil that generates a magnetic force when energized, a yoke that supports the electromagnetic coil, and an armature that is attracted to the yoke by the magnetic force, and the armature is attracted to the yoke. By applying the generated frictional force to the pressing member, the pressing member is rotated relative to the connecting member.
The clutch device according to any one of claims 1 to 3. The connecting member engages one of the first member and the second member with the connecting position and the non-connecting position,
The pressing member engages with the armature so as to be relatively movable in the axial direction and non-rotatable.
The rotational force imparting mechanism relatively rotates the coupling member and the pressing member that rotate according to the rotation of the first member or the second member by suppressing the rotation of the armature by the friction force.
The clutch device according to claim 4. The protrusion is provided on the pressing member;
The protrusion is inserted through an insertion hole formed in the armature.
The clutch device according to claim 5. The connecting member has a first spline engaging portion that is spline engaged with the first member on an inner peripheral surface, and a second spline engaging portion that is spline engaged with the second member on an outer peripheral surface.
The clutch device according to any one of claims 1 to 6.

Images