JP2012122563A - Engagement device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an engagement device which can enlarge the clearance between engaging members during release while suppressing the increase of electric power consumed when the engaging members are mutually engaged.SOLUTION: An engagement device 10A includes a first rotating member 11 having a clutch member 13, a second rotating member 12 provided with a base member 14 arranged so as to sandwich the clutch member 13 and a cam mechanism 15, and an electromagnetic coil 32 which generates a magnetic force which can drive the clutch member 13 to a position in contact with the second cam member 21 of the cam mechanism 15 when turned on, wherein the cam mechanism 15 has a first cam member 20 integrally rotates with the base member 14, and a second cam member 21 which can relatively rotates to the first cam member 20, when the second cam member 21 relatively rotates to the first cam member 20, pushes the second cam member 21 to the base member 14 side, by the second cam member 21, the clutch member 13 is compressed to the base member 14.

Description

  The present invention relates to an engaging device that allows or prevents power transmission between engaging members by engaging and separating a first engaging member and a second engaging member.

  There is known an engagement device that engages or separates an input-side engagement member and an output-side engagement member to switch a power transmission state between the engagement members. In addition, there is a pair of cam members, and when one cam member rotates relative to the other cam member, a force that presses one of the input side engagement member and the output side engagement member against the other is applied. An engagement device provided with a cam mechanism is known. For example, out of a pair of cam members configured such that the axial interval is increased by relative rotation, one cam member is attracted by the electromagnetic force of an electromagnetic coil and moved in the axial direction to promote relative rotation. As a result, there is known an engaging device that presses the cam member against a rotating member to be engaged to engage the engaging members with each other and increase the frictional engagement force between them (see Patent Document 1). .

JP 2004-060863 A

  In an engagement device such as that disclosed in Patent Document 1, in order to prevent one engagement member from being dragged by the rotation of the other engagement member when released, a gap between the engagement members is provided. It needs to be bigger. In this case, since it is necessary to increase the magnetic force to be generated by the electromagnetic coil when these engaging members are engaged with each other, power consumption may increase.

  Therefore, an object of the present invention is to provide an engagement device capable of expanding a gap between engagement members at the time of release while suppressing an increase in electric power consumed when the engagement members are engaged with each other. And

  The engagement device according to the present invention includes an engagement device provided with a first engagement member and a second engagement member that are relatively rotatable around a common axis, wherein the first engagement member is the axis. A clutch member made of a magnetic material provided so as to be movable in a direction, wherein the second engagement member is arranged so as to be aligned with the clutch member in the axial direction, and the first friction member The clutch member and the first friction member are arranged side by side in the axial direction so as to be sandwiched between the clutch member and the first friction member, and can rotate relative to the first friction member and move in the axial direction. And a second friction member made of a magnetic material, and when energized, a magnetic path is formed between the second friction member and the clutch member, and the clutch member is moved to the second friction by electromagnetic force. Electromagnetic drive to attract to the member A step, a first cam member that rotates integrally with the first friction member, and a first cam member that is disposed coaxially with the first cam member, and that is rotatable relative to the first cam member and movable in the axial direction. And a second cam member that rotates integrally with the second friction member, and the second friction member is moved to the first friction member when the second cam member rotates relative to the first cam member. And a cam mechanism that generates a pressing force to the side and presses the clutch member against the first friction member by the second friction member (claim 1).

  In the engagement device of the present invention, when the first engagement member and the second engagement member are engaged, first, the clutch member is attracted to the second friction member by the electromagnetic driving means. At this time, if the engagement device is configured to be able to control the torque transmitted between the engagement members, the clutch member and the second friction member are adjusted by adjusting the magnetic force generated by the electromagnetic drive means. The clutch member is adsorbed so as to slide at a different rotational speed while contacting with each other. In addition, what is necessary is just to change the magnetic force which should be generated with an electromagnetic drive means according to the torque which should be transmitted between engagement members. When there is no need to control the torque transmitted between the engaging members, the second friction member and the clutch member may be attracted so as to rotate integrally. That is, in the engagement device of the present invention, when the clutch member is attracted to the second friction member, the second friction member and the clutch member may be attracted so as to rotate integrally, or the clutch member and the second friction member may be attracted. You may make it adsorb | suck so that it may rotate with a mutually different rotation speed, slipping | sliding between members and contacting these. When the clutch member is attracted to the second friction member, the second cam member that rotates integrally with the second friction member rotates relative to the first cam member, so that the second friction member is moved to the first friction member side by the cam mechanism. The clutch member is pressed against the first friction member by the second friction member, and the first engagement member and the second engagement member are engaged.

  As described above, according to the engagement device of the present invention, it is only necessary that the electromagnetic driving means can generate a magnetic force capable of attracting the clutch member to the second friction member. Therefore, it can suppress that the electric power consumed by an electromagnetic drive means increases when engaging member is engaged. In the engagement device of the present invention, a gap can be provided both between the clutch means and the first friction member and between the clutch means and the second friction member. Therefore, the clearance gap between the 1st engagement member and the 2nd engagement member at the time of releasing can be expanded. Therefore, according to the engagement device of the present invention, it is possible to widen the gap between the engagement members at the time of release while suppressing an increase in power consumed when the engagement members are engaged with each other.

  In one form of the engaging device of the present invention, the second friction member and the second cam member may be arranged and integrated so as to be aligned in the axial direction (Claim 2). Since the number of parts of the engaging device can be reduced by integrating the second friction member and the second cam member in this manner, the cost can be reduced. Further, since the second friction member and the second cam member are arranged so as to be aligned in the axial direction, the number of components aligned in the axial direction can be reduced by integrating these members. Therefore, the axial dimension of the engagement device can be shortened.

  In this embodiment, the second cam member may be made of a magnetic material, and the second friction member and the second cam member may function as a yoke when the electromagnetic driving means is energized. In this case, the number of parts of the engaging device can be further reduced.

  In one form of the engagement device of the present invention, the cam mechanism is disposed so as to overlap a range of the first friction member to which the clutch member is pressed when the engagement device is viewed from the axial direction. (Claim 4). In this case, the force generated by the cam mechanism can be applied from the axial direction to a range where the first friction member and the clutch member are in contact with each other. Therefore, it can suppress that a clutch member contacts a 1st friction member and a 2nd friction member, and these deform | transform. Therefore, the lifetime of these parts can be extended. Further, the coefficient of friction between the clutch member and each friction member can be stabilized.

  In one embodiment of the engagement device of the present invention, the spring member further biases the clutch member so that the clutch member moves to a release position away from both the first friction member and the second friction member. It may be provided (claim 5). In this embodiment, when the electromagnetic attraction force or the force generated by the cam mechanism is not acting on the clutch means, the clutch means can be moved to the release position by the spring means, and the engagement device can be switched to the release state.

  As described above, according to the engagement device of the present invention, the electromagnetic driving unit only needs to generate a magnetic force that can attract the clutch member to the second friction member. At this time, a magnetic force that causes the clutch member and the second friction member to rotate together may be generated, or a slip occurs between the clutch member and the second friction member, causing them to come into contact with each other. Magnetic forces that rotate at different rotational speeds may be generated. Further, a gap can be provided both between the clutch means and the first friction member and between the clutch means and the second friction member. Therefore, it is possible to widen the gap between the engaging members at the time of release while suppressing an increase in power consumed when the engaging members are engaged with each other.

The figure which shows a part of power transmission device with which the engaging device which concerns on the 1st form of this invention was integrated. The figure which looked at the 2nd engaging part from the axial direction. The figure which looked at the 1st cam member and opposing part when the phase of a 1st cam member and a 2nd cam member corresponds from the radial direction outer side. The figure which looked at the 1st cam member and opposing part from the radial direction outer side when the phase of a 1st cam member and a 2nd cam member has shifted | deviated. The figure which shows the relationship between electromagnetic attraction force and torque capacity. The figure which shows the relationship between a cam angle and the largest transmission torque capacity of an engagement apparatus. The flowchart which shows operation | movement of each part of an engagement apparatus in the case of engaging a 1st rotation member and a 2nd rotation member. The figure which shows the engagement apparatus of the 1st form in an engagement state. The figure which shows the modification of the form shown in FIG. The figure which shows the engaging apparatus which concerns on the 2nd form of this invention. The figure which shows the engagement apparatus of the 2nd form in an engagement state.

(First form)
FIG. 1 shows a part of a power transmission device in which an engagement device according to a first embodiment of the present invention is incorporated. The power transmission device 1 is used by being incorporated in an automatic transmission of a vehicle, a power distribution device of a hybrid vehicle, or the like. The power transmission device 1 includes a first rotating shaft 2 and a second rotating shaft 3 extending in the direction of the axis Ax. The first rotating shaft 2 is supported by the case 4 via a bearing (not shown) so as to be rotatable about the axis Ax. The second rotating shaft 3 has a hollow cylindrical shape, and is provided around the first rotating shaft 2 and coaxially with the first rotating shaft 2. The second rotary shaft 3 is supported by the case 4 via a bearing (not shown) so as to be rotatable about the axis Ax and to be rotatable relative to the first rotary shaft 2. As shown in this figure, the first rotating shaft 2 is provided so that the tip thereof protrudes from the end of the second rotating shaft 3.

  In addition, the power transmission device 1 includes an engagement device 10 </ b> A for switching a power transmission state between the first rotation shaft 2 and the second rotation shaft 3. The engaging device 10A includes a first rotating member 11 as a first engaging member and a second rotating member 12 as a second engaging member. The engaging device 10A engages the rotating members 11 and 12 to allow power transmission between the rotating shafts 2 and 3, and separates the rotating members 11 and 12 to prevent power transmission. Switch state.

  The first rotating member 11 includes a clutch member 13 made of a magnetic material. The clutch member 13 has a hollow disk shape, and a spline 13a extending in the direction of the axis Ax is provided on the inner peripheral surface thereof. A spline 2 a that meshes with the spline 13 a of the clutch member 13 is provided on the outer peripheral surface at the tip of the first rotating shaft 2. The clutch member 13 is attached to the first rotary shaft 2 so that the spline 13a meshes with the spline 2a of the first rotary shaft 2. Thus, the clutch member 13 is attached to the first rotary shaft 2 so as to rotate integrally with the first rotary shaft 2 and to be movable in the direction of the axis Ax. Friction material is provided on the two surfaces 13b and 13c of the clutch member 13 facing the axis Ax direction.

  The second rotating member 12 includes a base member 14 attached to the second rotating shaft 3 and a cam mechanism 15. The base member 14 includes a hollow disc-shaped first engaging portion 16 and a hollow cylindrical cylindrical portion 17 extending from the outer peripheral end of the first engaging portion 16 in the axis Ax direction. As shown in this figure, the inner diameter of the cylindrical portion 17 is larger than the outer diameter of the clutch member 13, and the clutch member 13 is disposed inside the cylindrical portion 17. Accordingly, the first engaging portion 16 and the clutch member 13 are arranged so as to be aligned in the direction of the axis Ax. Nothing is arranged between the cylindrical portion 17 and the clutch member 13, and the cylindrical portion 17 is provided adjacent to the radially outer side of the clutch member 13. As shown in this figure, a bearing 18 is provided between the outer peripheral surface of the cylindrical portion 17 and the case 4, and the cylindrical portion 17 is supported by the case 4 via the bearing 18 so as to be rotatable around the axis Ax. Has been. A spline 16 a extending in the direction of the axis Ax is provided on the inner peripheral surface of the first engagement portion 16. A spline 3 a that meshes with the spline 16 a of the first engaging portion 16 is provided on the outer peripheral surface at the tip of the second rotating shaft 3. As shown in this figure, the base member 14 is attached to the second rotating shaft 3 so that the spline 16 a of the first engaging portion 16 is engaged with the spline 3 a of the second rotating shaft 3. Therefore, the base member 14 rotates integrally with the second rotating shaft 3. A friction material 19 is provided on a portion of the surface of the first engagement portion 16 facing the clutch member 13.

  The cam mechanism 15 includes a first cam member 20 attached to the base member 14, a second cam member 21 made of a magnetic material provided so as to be aligned with the first cam member 20 in the axis Ax direction, and the cam members 20. , 21 are provided with a plurality of cam balls 22 interposed therebetween. The first cam member 20 has a ring shape. As shown in this figure, the case 4 is provided with a cylindrical projection 5 made of a magnetic material that projects into the base member 14. The 1st cam member 20 is supported by the outer peripheral surface 5a of the protrusion part 5 so that rotation around the axis line Ax is possible. Further, a spline 20 a extending in the axis Ax direction is provided on the outer peripheral surface of the first cam member 20. A spline 17 a that meshes with the spline 20 a of the first cam member 20 is provided on the inner peripheral surface at the tip of the cylindrical portion 17 of the base member 14. The first cam member 20 is attached to the cylindrical portion 17 so that the spline 20 a meshes with the spline 17 a of the cylindrical portion 17. Therefore, the first cam member 20 rotates integrally with each of the base member 14 and the second rotating shaft 3. The cylindrical portion 17 is provided with a snap ring 23 for preventing the first cam member 20 from moving in a direction away from the first engaging portion 16 (left side in the drawing) from the position shown in the drawing. ing. A thrust bearing 24 is provided between the first cam member 20 and the case 4 to support the first cam member 20 so as to be rotatable from the direction of the axis Ax.

  The second cam member 21 includes a cylindrical cylindrical portion 25 disposed between the first cam member 20 and the clutch member 13 and a radially inner side from one end of the cylindrical portion 25 so as to face the first cam member 20. A ring-shaped cam portion 26 extending inward, and a second engagement portion 27 extending radially inward from the other end of the cylindrical portion 25 so as to face the clutch member 13. As shown in this figure, the second engagement portion 27 includes a contact portion 27a extending in the radial direction from one end of the cylindrical portion 25, a facing portion 27b extending in the axis Ax direction from the inner peripheral end of the contact portion 27a, And a bearing support portion 27c extending radially inward from the facing portion 27b. The facing portion 27b extends in a direction away from the clutch member 13 so that the outer peripheral surface thereof faces the inner peripheral surface 5b of the protruding portion 5. FIG. 2 is a view of the second engaging portion 27 as viewed from the direction of the axis Ax. As shown in this figure, the contact portion 27a is provided with a plurality of inhibition portions 27d. These blocking portions 27d are made of a non-magnetic material and are attached to the contact portion 27a by welding or the like. The plurality of inhibition portions 27d are arranged so as to be arranged at a predetermined interval on the same circumference around the axis Ax. Further, the plurality of inhibition portions 27d are arranged at the central portion in the radial direction so that the second engagement portions 27 are divided into a radially inner portion and a radially outer portion by the inhibition portions 27d.

  As shown in FIG. 1, the second cam member 21 includes a cam portion 26 that is coaxial with the first cam member 20 and arranged in the axis Ax direction, and a second engagement portion 27 that is connected to the clutch member 13 and the first engagement portion 16. They are provided so as to be aligned in the direction of the axis Ax. Therefore, as shown in this figure, the first cam member 20, the cam portion 26, the second engagement portion 27, the clutch member 13, and the first engagement portion 16 are arranged in this order in the axis Ax direction. Has been. Thus, the 1st engaging part 16 and the 2nd engaging part 27 are arrange | positioned so that the clutch member 13 may be pinched | interposed from the both sides of the axis line Ax direction.

  The inner diameter of the cylindrical portion 17 is larger than the outer diameter of the cam portion 26 and the outer diameter of the second engaging portion 27, and the cylindrical portion 17 is located on the radially outer side of the cam portion 26, the second engaging portion 27, and the clutch member 13. Is provided. The second cam member 21 is disposed such that the inner peripheral surface of the cam portion 26 is supported by the outer peripheral surface 5a of the protruding portion 5 and the outer peripheral surface of the facing portion 27b is located inside the inner peripheral surface 5b of the protruding portion 5. Has been. The second cam member 21 is supported by the case 4 so as to be rotatable about the axis Ax and movable in the direction of the axis Ax by being supported by the protruding portion 5 in this manner.

  The first cam member 20 is provided with the same number of V-shaped grooves 28 as the cam balls 22. The plurality of V-shaped grooves 28 are provided on the surface facing the cam portion 26 as shown in FIG. The plurality of V-shaped grooves 28 are arranged so as to be arranged at a predetermined interval on the same circumference. The cam portion 26 is provided with a plurality of V-shaped grooves 29 having the same number and the same shape as the V-shaped grooves 28 of the first cam member 20. The plurality of V-shaped grooves 29 are provided on the surface facing the first cam member 20. The plurality of V-shaped grooves 29 are arranged on the circumference having the same diameter as the circumference where the plurality of V-shaped grooves 28 of the first cam member 20 are arranged so as to be arranged at the same intervals as the plurality of V-shaped grooves 28. ing. The plurality of cam balls 22 are interposed between the first cam member 20 and the cam portion 26 and are held by the plurality of V-shaped grooves 28 and 29. 3 and 4 show the first cam member 20 and the cam portion 26 as viewed from the outside in the radial direction. 3 shows a state in which the phases of the first cam member 20 and the second cam member 21 are in agreement, and FIG. 4 shows a state in which the phases of the first cam member 20 and the second cam member 21 are shifted. Each is shown. As shown in FIG. 1, each V-shaped groove 28 and 29 has a semicircular cross section when cut along a cross section including the axis Ax. 3 and 4, when viewed from the radial direction, each V-shaped groove 28, 29 is formed in a V-shape, and the rotation direction of each rotary shaft 2, 3 (upward or downward direction in the figure). ), The depth gradually decreases.

  As shown in FIG. 1, a first return spring 30 that pushes the clutch member 13 in a direction away from the first engaging portion 16 is provided between the first engaging portion 16 and the clutch member 13 of the second rotating member 12. It has been. The first return spring 30 is provided with a bearing 30a so that the clutch member 13 and the first engagement portion 16 can rotate separately. A second return spring 31 that pushes the clutch member 13 in a direction away from the second engagement portion 27 is provided between the second engagement portion 27 of the second rotation member 12 and the clutch member 13. The second return spring 31 is also provided with a bearing 31a so that the clutch member 13 and the second engagement portion 27 can rotate separately. As shown in the drawing, the return springs 30 and 31 are arranged on the radially inner side with respect to the protruding portion 5. These return springs 30 and 31 push the clutch member 13 with substantially the same force from the left and right directions in the figure. Therefore, when no force other than the return springs 30 and 31 is acting on the clutch member 13 from the direction of the axis Ax, the return springs 30 and 31 cause the clutch member 13 to engage with the first engagement portion 16 and the second engagement. It is driven to a position away from both of the parts 27. Hereinafter, this position may be referred to as a release position. Therefore, these return springs 30 and 31 correspond to the spring means of the present invention. When the clutch member 13 is in the release position, gaps are generated between the clutch member 13 and the first engagement portion 16 and between the clutch member 13 and the second engagement portion 27, respectively. Therefore, the 1st rotation member 11 and the 2nd rotation member 12 can rotate separately, respectively.

  The protruding portion 5 of the case 4 is provided with an electromagnetic coil 32 as electromagnetic driving means. As shown in this figure, the electromagnetic coil 32 is disposed inside the second cam member 21 so that the cam portion 26 is located on one side in the direction of the axis Ax and the second engagement portion 27 is located on the other side. ing. The width of the electromagnetic coil 32 in the direction of the axis Ax is large enough to move the second cam member 21 to a position where the second cam member 21 presses the clutch member 13 against the first engaging portion 16 when the second cam member 21 moves to the right side in FIG. Is set. The electromagnetic coil 32 is configured to generate a magnetic force that can attract the clutch member 13 to the second engagement portion 27 against the second return spring 31 when energized.

  In this engagement device 10A, as shown in FIG. 4, when the phases of the first cam member 20 and the second cam member 21 shift, the cam ball 22 moves to a shallow position in the V-shaped grooves 28 and 29, and the second cam A force F (hereinafter sometimes referred to as a pressing force) F that pushes the member 21 away from the first cam member 20 is generated. In this case, the second cam member 21 is pressed toward the first engagement portion 16 (the right side in FIG. 1), and the second engagement portion 27 is pressed against the clutch member 13. In addition, the clutch member 13 is thereby pressed against the first engagement portion 16, and the clutch member 13 is sandwiched between the first engagement portion 16 and the second engagement portion 27 from both sides in the axis Ax direction. In this way, the clutch member 13 is attracted to the second engaging portion 27 or pressed against the first engaging portion 16, whereby the first rotating member 11 and the second rotating member 12 are engaged, and the power is generated between them. (Torque) is transmitted.

  And in this engagement apparatus 10A, even if it stops the electricity supply to the electromagnetic coil 32, after the clutch member 13 is pinched | interposed into each engaging part 16 and 27 by setting various specifications suitably, the state is the same Can be selected, and a non-self-locking method in which the engagement of the clutch members 13 by the engaging portions 16 and 27 that stop energizing the electromagnetic coil 32 is released. In the self-locking method, when the clutch member 13 is pressed against the first engaging portion 16, no slip occurs between the clutch member 13 and the first engaging portion 16, and each specification is set so that they rotate integrally. Is set.

  On the other hand, in the non-self-locking method, various types of slips can be generated between the clutch member 13 and the first engagement portion 16 even when the clutch member 13 is pressed against the first engagement portion 16. The origin is set. Therefore, in the non-self-locking method, the clutch member 13 and each of the engaging portions 16 and 27 are caused by slipping between the clutch member 13 and the second engaging portion 27 by weakening the magnetic force generated by the electromagnetic coil 32. Can be brought into a so-called half-clutch state in which power is transmitted between them while rotating at different rotational speeds. In the engaging device 10A, the pressing force F increases as the torsional torque generated between the first cam member 20 and the second cam member 21 increases. Further, the electromagnetic attraction force that attracts the clutch member 13 to the second engagement portion 27 increases as the current supplied to the electromagnetic coil 32 increases. As the electromagnetic attraction force is increased and the rotational speed difference between the clutch member 13 and the second engagement portion 27 is reduced, the torsion torque generated in the cam mechanism 15 is increased. The difference in rotational speed between 16 and 27 is reduced, and the torque capacity transmitted between them is increased. FIG. 5 shows the relationship between the electromagnetic attractive force and the torque capacity. As shown in this figure, in the non-self-locking system, there is a correlation between the torque capacity transmitted between the clutch member 13 and the engaging portions 16 and 27 and the electromagnetic attractive force acting on the clutch member 13. Yes, the torque capacity can be controlled by adjusting the electromagnetic attractive force. Since the electromagnetic attractive force is proportional to the magnitude of the current supplied to the electromagnetic coil 32 as described above, the torque capacity changes according to the magnitude of the current supplied to the electromagnetic coil 32.

  The specifications that determine these types of the engaging device 10A are in contact with each other at, for example, the cam angle θ (see FIGS. 3 and 4) of the V-shaped grooves 28 and 29, the clutch member 13, and the engaging portions 16 and 27. These are the friction coefficient of the portion, the friction radius of the clutch member 13 and the engaging portions 16 and 27, and the like. FIG. 6 shows the relationship between the cam angle θ and the maximum transmission torque capacity Tmax of the engagement device 10. It should be noted that other specifications such as the friction coefficient and the friction radius are constant as the conditions of the relationship shown in this figure. The self-lock angle θSL shown in this figure is a value of 0 degree or more, and the phase of the first cam member 20 and the second cam member 21 is shifted and the clutch member 13 is pressed against the first engagement portion 16. In this case, the cam angle θ is such that the first rotating member 11 and the second rotating member 12 rotate integrally without slippage between the clutch member 13 and the first engaging portion 16. Therefore, when the cam angle θ is the self-locking angle θSL, the engaging device 10A becomes the self-locking method, and when the cam angle θ is larger than the self-locking angle θSL, the engaging device 10A becomes the non-self-locking method. As shown in this figure, the maximum transmission torque capacity Tmax becomes maximum when the cam angle θ is the self-lock angle θSL, and decreases as the cam angle θ becomes larger.

  Next, the operation of the engagement device 10A will be described with reference to FIG. 1, FIG. 7, and FIG. FIG. 7 is a flowchart showing how each part of the engagement device 10A operates when the first rotating member 11 and the second rotating member 12 are engaged. FIG. 8 shows the engagement device 10A in the engaged state. 8 that are the same as those in FIG. 1 are denoted by the same reference numerals and description thereof is omitted. As described above, in the engagement device 10A, the self-locking method and the non-self-locking method can be selected. First, the operation of the non-self-locking engagement device 10A will be described.

  When engaging the first rotating member 11 and the second rotating member 12 as shown in step S <b> 1 of FIG. 7, first, the electromagnetic coil 32 is energized. As a result, a magnetic circuit (magnetic path) MC is formed around the electromagnetic coil 32 as indicated by a broken line in FIG. As described above, since the inhibition portion 27d is a non-magnetic material, the magnetic force flows from the second engagement portion 27 of the second cam member 21 to the clutch member 13. Therefore, the magnetic path MC is formed between the clutch member 13, the second cam member 21, and the protruding portion 5. At this time, the magnetic path MC flows from the clutch member 13 to the protruding portion 5 through the facing portion 27 b of the second engaging portion 27. When the magnetic path MC is thus formed, the clutch member 13 is attracted toward the second cam member 21 as shown in step S2. Then, as shown in step S <b> 3, the clutch member 13 is attracted to the second engagement portion 27. As described above, in the case of the non-self-locking method, the torque capacity can be controlled by adjusting the electromagnetic attractive force. Therefore, when the clutch member 13 is attracted to the second engaging portion 27 in this way, the amount of current supplied to the electromagnetic coil 32 can be adjusted to generate an electromagnetic attraction force that achieves the target torque capacity. That's fine.

  When the clutch member 13 is attracted to the second engagement portion 27, torque transmission to the cam ball 22 is started as shown in step S4. Thereby, the phase of the 1st cam member 20 and the 2nd cam member 21 begins to shift. As shown in FIG. 4, when the cam members 20 and 21 are out of phase, a pressing force F is generated. Then, as shown in step S <b> 5, the second cam member 21 and the clutch member 13 are moved toward the first engagement portion 16 by the pressing force F. In this case, the distance between the second cam member 21 and the protruding portion 5 is increased in the axis Ax direction, but is maintained at substantially the same distance in the radial direction. As shown in FIG. 1, since the cam portion 26 of the second cam member 21 is supported by the protruding portion 5, the distance between the protruding portion 5 and the cam portion 26 hardly changes. Even if the second cam member 21 moves in the direction of the axis Ax, the facing portion 27b only slides in the direction of the axis Ax. Therefore, the distance between the facing portion 27b and the inner peripheral surface 5b of the projecting portion 5 is almost the same. It does not change. Therefore, even when the second cam member 21 moves in the axis Ax direction, the magnetic path MC is maintained, and the clutch member 13 is maintained in a state of being attracted to the second engagement portion 27. Thereafter, as shown in step S <b> 6, the clutch member 13 comes into contact with the first engagement portion 16. As a result, the clutch member 13 is pressed against the first engaging portion 16, and the engaging device 10A is switched to the state shown in FIG.

  In this case, as shown by broken lines FC1 and FC2 in the figure, one of the forces generated by the cam mechanism 15 is transmitted to the clutch member 13 via the second cam member 21, and the other is transmitted through the first cam member 20 and the base member 14. To the clutch member 13. The clutch member 13 is sandwiched between the first engaging portion 16 and the second engaging portion 27 of the second rotating member 12 by these forces. At this time, the clutch member 13 is pressed against the portion indicated by the range A in the first engagement portion 16. A frictional force is generated between the clutch member 13 and the first engagement portion 16 and between the clutch member 13 and the second engagement portion 27 in a region overlapping with the range A when viewed from the axis Ax direction. As a result, the first rotating member 11 and the second rotating member 12 rotate integrally, so that torque capacity is generated in the entire engaging device 10A as shown in step S7, and the first rotating member 11 and the second rotating member are generated. The engagement with 12 is completed. However, even before the torque capacity is generated in the entire engaging device 10A, the torque capacity corresponding to the inertia of each component is generated.

  When the non-self-locking type engagement device 10A is switched from the engaged state to the released state, the energization to the electromagnetic coil 32 is stopped. As a result, the magnetic path MC disappears, so that the electromagnetic attractive force acting between the clutch member 13 and the second cam member 21 disappears. When the electromagnetic attractive force disappears, slippage occurs between the clutch member 13 and the first engaging portion 16, and the rotation of the first rotating shaft 2 is hardly transmitted to the second cam member 21. Therefore, the phase shift between the first cam member 20 and the second cam member 21 is reduced. As a result, the pressing force F is reduced, and the clutch member 13 is moved to the release position by the return springs 30 and 31. As a result, the engaging device 10A is switched to the released state.

  Next, the operation of the self-locking engagement device 10A will be described. Even in this case, the procedure for switching the engaging device 10A to the engaged state is the same as that of the non-self-locking method described above. However, since the torque capacity cannot be adjusted in the case of the self-locking method, in step S1, the electromagnetic coil 32 is caused to generate an electromagnetic attractive force that causes the clutch member 13 and the second engaging portion 27 to rotate integrally. Current is supplied. As a result, a pressing force F is generated, so that the clutch member 13 is pressed against the first engaging portion 16 to switch to the engaged state shown in FIG. The pressing force F continues to be generated while the first cam member 20 and the second cam member 21 are out of phase. In the self-locking system, each item is set so that no slip occurs between the clutch member 13 and the first engaging portion 16. Therefore, in the self-locking method, the first rotating member 11 and the second rotating member 12 are kept engaged while the clutch member 13 is in contact with the first engaging portion 16 or the second engaging portion 27. Is done.

  As described above, in the case of the self-locking method, if there is a rotational speed difference between the first rotating member 11 and the second rotating member 12, the cam mechanism 15 keeps the clutch member 13 locked. Therefore, in order to switch the engagement device 10A from the engaged state to the released state, the energization to the electromagnetic coil 32 is stopped and the rotation speeds of the first rotating shaft 2 and the second rotating shaft 3 are made the same. In addition, you may make these rotation speeds the same by stopping these rotating shafts 2 and 3. FIG. As a result, the clutch member 13 is moved to the release position by the return springs 30 and 31, so that the engagement device 10A is switched to the release state.

  As described above, in the engaging device 10A of the present invention, when the first rotating member 11 and the second rotating member 12 are engaged, the clutch member 13 is first moved by the magnetic force generated by the electromagnetic coil 32. 2 Contact with the engaging portion 27. Thereafter, the clutch member 13 is sandwiched between the first engaging portion 16 and the second engaging portion 27 by the pressing force F generated by the cam mechanism 15, and the rotating members 11 and 12 are engaged with each other. Thus, the electromagnetic coil 32 only needs to be able to generate a magnetic force that can cause the clutch member 13 to be attracted to the second engaging portion 27, and therefore is consumed by the electromagnetic coil 32 when the rotating members 11, 12 are engaged with each other. An increase in power can be suppressed. In the case of the non-self-locking method, an electromagnetic attractive force corresponding to a target torque capacity may be generated, and an electromagnetic attractive force that causes the clutch member 13 and the second engaging portion 27 to rotate integrally is necessarily generated. Since there is no need, an increase in power can be further suppressed. Further, as shown in FIG. 1, when the clutch member 13 is in the released position, there is a gap between both the clutch member 13 and the first engagement portion 16 and between the clutch member 13 and the second engagement portion 27. Can be provided. Therefore, the gap between the first rotating member 11 and the second rotating member 12 can be widened. As a result, it is possible to prevent one of the first rotating member 11 and the second rotating member 12 from being dragged and rotated by the other rotation, and thus torque generated by one of the first rotating member 11 and the second rotating member 12 being rotated by the other, So-called drag torque can be reduced. On the other hand, when the first rotating member 11 and the second rotating member 12 are engaged, the clutch member 13 is engaged with both the first engaging portion 16 and the second engaging portion 27, so that transmission is possible. Torque capacity can be increased. Since the clutch member 13 is thus engaged, the first engagement portion 16 corresponds to the first friction member of the present invention, and the second engagement portion 27 corresponds to the second friction member of the present invention. The cam portion 26 of the second cam member 21 corresponds to the second cam member of the present invention.

  As shown in FIG. 1, in the engagement device 10 </ b> A, the second cam member 21 is made of a magnetic material and is a component that becomes the magnetic path MC when the electromagnetic coil 32 is energized. Therefore, the second cam member 21 functions as a part of the cam mechanism 15 and also functions as a yoke for increasing the magnetic force of the electromagnetic coil 32. The second cam member 21 is also provided with a second engagement portion 27 that contacts the clutch member 13. Thus, in the engaging device 10A, the second cam member 21 has a plurality of functions. Thereby, since the number of parts of 10 A of engagement apparatuses can be reduced, cost can be reduced. Further, as shown in FIG. 1, since the cam portion 26 and the second engaging portion 27 are arranged side by side in the axis Ax direction, the number of components arranged in the axis Ax direction can be reduced by integrating these components. Therefore, the dimension of the engaging device 10A in the axis Ax direction can be shortened.

  In this engagement device 10A, as shown in FIGS. 1 and 8, the cam ball 22 is disposed so as to overlap the range A where the clutch member 13 is pressed against the first engagement portion 16 when viewed from the direction of the axis Ax. . Therefore, the force FC1 generated by the cam mechanism 15 can be applied to the portion of the range A of the clutch member 13 from the direction of the axis Ax. As a result, the clutch member 13 can be prevented from being biased against the first engaging portion 16 and the second engaging portion 27 and the deformation thereof can be suppressed, so that the clutch member 13, the first engaging portion 16 and the second engaging portion can be suppressed. It is possible to suppress a force from being concentrated on a part of the joint portion 27 and an excessive surface pressure. Therefore, the lifetime of these parts can be extended. In addition, the friction coefficient between the clutch member 13 and the first engagement portion 16 and the second engagement portion 27 can be stabilized thereby, so that the clutch member 13 is connected to the first engagement portion 16 or the second engagement portion. It is possible to suppress erroneous engagement with the joint portion 27 or occurrence of a release failure of the engagement device 10A.

  The position where the plurality of cam balls 22 are arranged is not limited to the position described above. The plurality of cam balls 22 may be arranged at various positions within the range A shown in FIG. 1 when the engagement device 10 is viewed from the direction of the axis Ax. For example, as shown in FIG. 9, as long as it is within the range A, the V-shaped grooves 28 and 29 and the cam balls 22 may be disposed radially inward from the above-described configuration. In this figure, the position where the cam ball 22 is arranged in the above-described form as a comparative example is indicated by an imaginary line. Thus, even if the positions of the plurality of cam balls 22 are changed radially inward, if the cam balls 22 are within the range A when viewed from the direction of the axis Ax, the force FC1 generated by the cam mechanism 15 is applied to the range of the clutch member 13. The portion A can be applied from the direction of the axis Ax. Therefore, also in this case, it is possible to suppress the clutch member 13 from being biased to the first engagement portion 16 and the second engagement portion 27 and from being deformed. Therefore, the lifetime of these parts can be extended.

(Second form)
Next, an engagement device 10B according to a second embodiment of the present invention will be described with reference to FIGS. 10 shows the engagement device 10B in the released state, and FIG. 11 shows the engagement device 10B in the engaged state. In addition, in this form, the same code | symbol is attached | subjected to the same part as the form mentioned above, and description is abbreviate | omitted. As shown in FIG. 10, the engagement device 10 </ b> B is different from the above-described embodiment in that a multi-plate clutch mechanism 40 is provided between the clutch member 13 and the first engagement portion 16.

  As shown in this figure, the clutch mechanism 40 includes a first clutch plate 41 provided on the clutch member 13 and a second clutch plate 42 provided on the base member 14. A protrusion 43 extending in the direction of the axis Ax is provided on the surface of the clutch member 13 on the first engagement portion 16 side. As shown in this figure, the protrusion 43 is provided on the radially inner side of the clutch mechanism 40. The first clutch plate 41 is attached to the protrusion 43 so as to rotate integrally with the clutch member 13 and be movable in the direction of the axis Ax. For example, the first clutch plate 41 and the protrusion 43 may be provided with splines extending in the axis Ax direction, and the first clutch plate 41 may be attached to the protrusion 43 so that the splines mesh with each other. The second clutch plate 42 is attached to the base member 14 so as to rotate integrally with the base member 14 and be movable in the direction of the axis Ax. Similarly to the first clutch plate 41, the second clutch plate 42 is attached by providing a spline extending in the direction of the axis Ax in each of the base member 14 and the second clutch plate 42, and the second clutch plate so that the splines mesh with each other. 42 may be attached to the base member 14.

  As shown in this figure, the first clutch plate 41 is provided between the second clutch plate 42 and the first engaging portion 16, and the second clutch plate 42 is provided between the first clutch plate 41 and the clutch member 13. Provided. That is, these portions are provided in the order of the clutch member 13, the second clutch plate 42, the first clutch plate 41, and the first engaging portion 16 in the order of the axis Ax.

  Next, the operation of the engagement device 10B will be described. In this engagement device 10B as well, the self-locking method and the non-self-locking method are selected by appropriately setting various parameters such as the cam angle θ, the friction coefficient, and the friction radius, as in the first embodiment. can do. First, the case of the non-self-locking method will be described. Even in the engaging device 10B, when switching from the released state to the engaged state, the electromagnetic coil 32 is energized to excite it. As a result, the clutch member 13 is attracted to the second engaging portion 27. The electromagnetic attractive force at this time may be set as appropriate according to the target torque capacity as in the first embodiment. When the clutch member 13 is attracted to the second engagement portion 27, a pressing force F is generated by the cam mechanism 15 and the clutch member 13 is pushed toward the first engagement portion 16 side. As shown in FIG. 11, the first clutch plate 41 is sandwiched between the second clutch plate 42 and the first engaging portion 16, and the second clutch plate 42 is sandwiched between the first clutch plate 41 and the clutch member 13. It is. This completes the switch to the engaged state. In this embodiment as well, the non-self-locking method can correlate the electromagnetic attractive force and the torque capacity as shown in FIG. 5, and therefore the torque capacity can be controlled by adjusting the electromagnetic attractive force. . When the non-self-locking type engagement device 10B is switched from the engaged state to the released state, the energization to the electromagnetic coil 32 may be stopped. As a result, the pressing force F is reduced, so that the clutch member 13 is moved to the release position by the return springs 30 and 31, and the engagement device 10B is switched to the release state.

  Similarly, in the self-locking type engagement device 10B, the electromagnetic coil 32 is energized when the state is switched from the released state to the engaged state. However, at this time, an electric current is supplied to the electromagnetic coil 32 so that an electromagnetic attractive force that causes the clutch member 13 and the second engaging portion 27 to rotate together is generated. As a result, a pressing force F is generated, and the clutch member 13 is pushed toward the first engaging portion 16 to switch to the engaged state shown in FIG. Even in this embodiment, in the self-locking system, the first rotating member 11 and the second rotating member 12 are engaged while the clutch member 13 is in contact with the first engaging portion 16 or the second engaging portion 27. Maintained. When the self-locking type engaging device 10B is switched from the engaged state to the released state, the energization to the electromagnetic coil 32 is stopped, and the rotary shafts 2 and 3 are stopped, for example. The number of rotations with the second rotating shaft 3 is made the same. As a result, the clutch member 13 is moved to the release position by the return springs 30 and 31, so that the engagement device 10B is switched to the release state.

  As described above, according to the second embodiment, the first clutch plate 41 is sandwiched between the second clutch plate 42 and the first engagement portion 16 when the engagement state is switched, and the second clutch plate 42 is in the first state. It is sandwiched between the clutch plate 41 and the clutch member 13. Thereby, since the contact area of the clutch member 13 and the base member 14 can be increased, the coupling force between the 1st rotation member 11 and the 2nd rotation member 12 can be strengthened. Therefore, the torque capacity that can be transmitted can be further increased as compared with the above-described embodiment.

  This invention is not limited to each form mentioned above, It can implement with a various form. For example, in each embodiment described above, the second cam member, which is a part of the cam mechanism, functions as a yoke, but the cam member and the yoke may be separate members. In this case, the cam member and the yoke are coupled so as to rotate integrally around the axis and to move integrally in the axial direction. By providing the cam member and the yoke in this manner, the first rotating member and the second rotating member can be engaged with each other by the electromagnetic coil and the cam mechanism as in the above-described embodiments.

  In each of the embodiments described above, the engagement device is used as a clutch that allows or prevents power transmission between the first rotation shaft and the second rotation shaft. However, the engagement device of the present invention is a first rotation member. Alternatively, one of the second rotating members may be fixed to be non-rotatable and used as a brake.

  In each embodiment described above, the cam mechanism using the cam ball is shown, but the cam mechanism provided in the engagement device of the present invention is not limited to this. It has a pair of cam members that can rotate relative to each other, and when the phase of the pair of cam members is shifted, the distance between the cam members can be increased using the torque acting on one of the cam members. Various possible cam mechanisms may be used.

10A, 10B Engaging device 11 First rotating member (first engaging member)
12 Second rotating member (second engaging member)
13 Clutch member 15 Cam mechanism 16 First engagement portion (first friction member)
20 First cam member 26 Cam portion (second cam member)
27 Second engaging portion (second friction member)
30 First return spring (spring means)
31 Second return spring (spring means)
32 Electromagnetic coil (Electromagnetic drive means)
Ax axis MC Magnetic circuit (magnetic path)
A Range where the clutch member is pressed in the engaging part

Claims (5)

In an engagement device including a first engagement member and a second engagement member that are provided to be relatively rotatable around a common axis,
The first engagement member includes a clutch member made of a magnetic material provided to be movable in the axial direction,
The second engagement member includes a first friction member provided to be aligned with the clutch member in the axial direction, and the clutch member and the clutch member so that the clutch member is sandwiched between the first friction member and the first friction member. A second friction member made of a magnetic material provided side by side in the axial direction with the first friction member, and capable of rotating relative to the first friction member and movable in the axial direction;
An electromagnetic drive means for forming a magnetic path between the second friction member and the clutch member when energized, and for attracting the clutch member to the second friction member by electromagnetic force; and the first friction member; A first cam member that rotates integrally with the first cam member, and is disposed coaxially with the first cam member so as to be rotatable relative to the first cam member and movable in the axial direction, and is integrated with the second friction member. A second cam member that rotates toward the first friction member when the second cam member rotates relative to the first cam member to generate a force that pushes the second friction member toward the first friction member. And a cam mechanism that presses the clutch member against the first friction member by a second friction member.   2. The engagement device according to claim 1, wherein the second friction member and the second cam member are arranged and integrated so as to be aligned in the axial direction. The second cam member is made of a magnetic material;
The engagement device according to claim 2, wherein the second friction member and the second cam member function as a yoke when the electromagnetic driving means is energized.   The said cam mechanism is arrange | positioned so that it may overlap with the range where the said clutch member is pressed among the said 1st friction members when the said engaging device is seen from the said axial direction. The engagement device described in 1.   The spring means which urges | biases the said clutch member so that the said clutch member may move to the release position away from both the said 1st friction member and the said 2nd friction member is provided. The engagement device according to item.

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