JP2010065813A - Rotation transmitting device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To smoothly achieve the transition from the engaged state of a two-way clutch to a racing state. <P>SOLUTION: In this rotation transmitting device, the two-way clutch 10 and an electromagnetic clutch 20 are assembled between an input side member 1 and an output side member 2. The two-way clutch 10 includes a cage 4, an engagement element 3 and a switch spring 5. The electromagnetic clutch 20 includes an armature 21, a rotor 22, an electromagnet 23 making the rotor 22 attract the armature 21 by energization, and a separating spring 24 for pressing the armature 21. The armature 21 includes a projecting part 31, and the input side member 1 includes a recessed part 32. When the armature 21 is separated from the rotor 22 by releasing the above energization, the projecting part 31 is fitted to the recessed part 32, thereby whirl-stopping the armature 21 to the input side member 1. A circumferential gap w is provided between the projecting part 31 and the recessed part 32, and the size of the gap w is determined according to the maximum acceleration caused during the transition from the engageed state to the racing state. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a rotation transmission device used for switching between transmission and cutoff of power in a power transmission path.

  As this type of rotation transmission device, one described in Patent Document 1 is known. In this rotation transmission device, an outer member as an output member is provided outside an inner member as an input member, a two-way clutch is incorporated between the inner member and the outer member, and the two-way clutch is turned on. , OFF is controlled by an electromagnetic clutch.

  Here, the two-way clutch is provided with a cam surface that forms a wedge-shaped space between the outer surface of the inner member and the cylindrical surface formed on the inner periphery of the outer member, and between the cam surface and the cylindrical surface. A roller as an engagement member incorporated in the inner member and the outer member is held by a retainer, and a spring force of a switch spring is applied to the retainer so that the roller The cage is elastically held so as to be in a neutral position where the engagement with the cylindrical surface is released.

  On the other hand, the electromagnetic clutch attracts and holds the armature that is prevented from rotating with respect to the cage and supported so as to be movable in the axial direction by energization of the electromagnetic coil of the electromagnet to the rotor that is prevented from rotating around the outer member. The vessel is coupled to the outer member.

  In the rotation transmission device configured as described above, when the armature is attracted to the rotor by energizing the electromagnetic coil of the electromagnetic clutch, the cage rotates relative to the inner member by the frictional resistance acting on the attracting surface, and the roller is cylindrical. The rotation of the inner member is transmitted to the outer member via the roller by engaging with the surface and the cam surface.

  Further, when energization of the electromagnetic coil of the electromagnet is released, the cage is returned to the neutral position by the spring force (restoring elasticity) of the switch spring, the engagement of the roller surface with the cylindrical surface and the cam surface is released, and the inner member is Idle.

  In this rotation transmission device, when the inner member rotates at high speed, the inner member and the roller held by the cage rotate together, and the roller moves radially outward by the centrifugal force acting on the roller. Because of the drag torque acting on the cylindrical surface of the outer member and acting on the contact portion, the inner member and the cage may rotate relative to each other, and the roller may be misengaged with the cam surface and the cylindrical surface. The power points are left.

  Further, when the inner member is rapidly accelerated and decelerated in the idling state, the inner member, the retainer, the armature and the inner member are elastically coupled to the inner member by the inertia force of the retainer, the armature and the roller. A difference in rotational speed is generated between the roller, the inner member, the cage, the armature, and the roller rotate relative to each other, and the roller may be misengaged with the cam surface and the cylindrical surface.

  Therefore, in order to prevent the misengagement, a convex portion is provided on one of the armature and the inner member, and a concave portion is provided on the other. When the armature is separated from the rotor by deenergizing the electromagnetic coil of the electromagnetic clutch, the convex portion Is fitted to the recess, and the armature is prevented from rotating with respect to the inner member by the fitting so that the cage can be maintained in the neutral position (for example, Patent Document 1, Patent Document 1). 2).

JP 2007-247713 A US Pat. No. 6,595,337

  According to the rotation transmission devices described in Patent Literatures 1 and 2, when the two-way clutch is about to shift from the engaged state to the idle state, the unevenness between the armature and the input side member (the inner member) is smooth. May not fit.

  This point will be described. When the two-way clutch is about to shift from the engaged state to the idling state, the cage and the engaging element are engaged with the input side member and the output side member by the restoring elasticity of the switch spring. From the neutral position to the neutral position. As the retainer rotates, the armature that is prevented from rotating by the retainer also rotates in the same direction by the same angle.

  However, after the energization of the electromagnetic clutch is released, the input side member continues to rotate even during a short period of time until the convex portion fits into the concave portion, and in particular, a large acceleration / deceleration occurs in the input side member. In some cases, a difference in rotational speed tends to occur between the input side member and the armature.

Further, when the input side member is rotating at a high speed, the engagement torque may be moved outward in the radial direction by the centrifugal force acting on the engagement element, and the drag torque for the output side member may be generated. For this reason, even when the input side member rotates at a high speed, a difference in rotational speed between the input side member and the armature tends to occur.
Conversely, when the output side member rotates faster than the rotational speed of the input side member, a similar drag torque may occur with respect to the input side member.

  If there is a rotational speed difference between the input side member and the armature, the phase of the input side member and the armature is shifted, and the unevenness of the input side member and the armature becomes difficult to fit smoothly. If the unevenness does not fit smoothly, there arises a problem that the two-way clutch cannot smoothly shift from the engaged state to the idle state.

  Accordingly, an object of the present invention is to smoothly shift the two-way clutch from the engaged state to the idle state.

  In order to solve the above-described invention, the present invention is a two-way system in which a rotational torque is transmitted and cut off between an input side member and an output side member provided outside the input side member. The two-way clutch includes an electromagnetic clutch that controls engagement and disengagement, and the two-way clutch includes a cage assembled between the input-side member and the output-side member, and the holding thereof. An engaging member that is held between the opposing surfaces of the input side member and the output side member by relative rotation of the cage with respect to the input side member and elastically deforms by the relative rotation. A switch spring for returning the retainer to a neutral position where the engagement element is disengaged by the restoring elasticity, and the electromagnetic clutch is moved in the axial direction of the two-way clutch with respect to the retainer. An armature that is free to rotate with respect to the cage, a rotor that is locked against the output-side member and faces the armature in the axial direction, and that the rotor faces the axial direction and is energized and energized. An electromagnet that attracts the armature to the rotor; and a separation spring that presses the armature in a direction away from the rotor. The electromagnetic clutch includes a convex portion on one of the armature and the input side member, and a concave portion on the other. When the armature is separated from the rotor by de-energizing to the rotor, the convex portion is fitted into the concave portion, and the fitting prevents the armature from rotating with respect to the input side member, so that the cage is in the neutral position. When the energization of the electromagnetic clutch is released in the rotation transmission device maintained at After the armature away from the rotor comes into contact with the input side member, when the phase of the convex portion and the concave portion first matches, a gap that allows the convex portion to fit into the concave portion is a gap between the convex portion and the concave portion. A rotation transmission device characterized by being provided between them was adopted.

According to this configuration, since the circumferential gap is interposed between the convex portion and the concave portion, even if there is a rotational speed difference between the input side member and the armature, the convex portion easily enters the concave portion. . If there is a gap, even if there is a slight phase shift (direction around the axis with respect to the axis of the two-way clutch) between the convex part and the concave part, the convex part fits into the concave part with the phase shifted. This is because they can match.
The convex portion may be provided on the input side member and the concave portion may be provided on the armature, or the concave portion may be provided on the input side member and the convex portion may be provided on the armature.

In addition, since various rotation transmission devices have different characteristics depending on the type and application, the acceleration and rotation speed of the input side member, or the input side member and the output side member are shifted from the engaged state to the idle state. Time varies.
For this reason, if the size of the gap is set according to the acceleration, the number of rotations, and the transition time that can occur in the rotation transmission device, an effect that the application range of the rotation transmission device can be expanded can be expected.

  In this configuration, the size of the gap may be determined based on the maximum acceleration that can be generated in the input side member while the two members shift from the engaged state to the idle state.

  Similarly, the size of the gap may be determined based on the maximum number of rotations that can be generated in the input side member while the two members shift from the engaged state to the idle state.

The rotational speed difference that can occur between the input side member and the armature is larger if the maximum acceleration that can be generated in the input side member during the transition from the engaged state to the idle state is large. Also, when the maximum rotational speed is large, it tends to appear as a larger rotational speed difference.
For this reason, it is desirable to set the size of the gap at which the convex portion easily enters the concave portion under the rotation condition of the input side member where the largest rotational speed difference can appear.

  The size of the gap is expressed by the equation x = y / 250, where y (rpm) is the maximum number of rotations allowed for the input side member when fitting the convex portion and the concave portion. The numerical value of x obtained in step (b) is defined as a lower limit value x (mm), and is determined to be a numerical value equal to or greater than the lower limit value x (mm), and is an axis allowed to the input side member and the armature by the gap The upper limit is a numerical value at which the angle of relative rotation of the convex portion is 5 to 9 (deg) on both sides of the circumferential direction at the neutral point where the convex portion is located at the circumferential center of the two-way clutch in the concave portion. , It can be configured to be determined to be a numerical value below the upper limit value.

In the present invention, since a gap is provided between the convex portion and the concave portion provided on the input side member and the armature, even if there is a rotational speed difference between the input side member and the armature, the convex portion is It becomes easy to enter the recess. For this reason, the two-way clutch can be smoothly shifted from the engaged state to the idle state.
Moreover, the effect that the application range of a rotation transmission apparatus expands significantly by setting the magnitude | size of a clearance gap suitably can also be expected.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
As shown in FIG. 1, an input shaft (input-side member) 1 includes a drive shaft 1a that is driven and rotated by a drive device (not shown), and a cam ring 9 provided at a central portion in the axial direction of the drive shaft 1a. I have.

An outer ring (output side member) 2 is provided on the outer diameter side of the input shaft 1. The outer ring 2 and the input shaft 1 are supported relatively rotatably via bearings 7 and 8.
The outer ring 2 can be rotatably supported in a housing (not shown) via another bearing.

  A two-way clutch 10 is provided between the input shaft 1 and the outer ring 2, and an electromagnetic clutch 20 that controls engagement and disengagement of the two-way clutch 10 is provided in parallel with the two-way clutch 10. .

  As shown in FIG. 3, the two-way clutch 10 forms a cylindrical surface 12 on the inner periphery of the outer ring 2, and a plurality of cam surfaces that form a wedge-shaped space with the cylindrical surface 12 on the outer periphery of the cam ring 9. 11 is provided at intervals in the circumferential direction, and a roller 3 as an engaging member is incorporated between each cam surface 11 and the cylindrical surface 12. Each roller 3 is held by a cage 4 incorporated between the input shaft 1 and the outer ring 2 to constitute a two-way roller clutch.

  Between the input shaft 1 and the cage 4, a switch spring 5 for elastically holding the cage 4 is incorporated at a neutral position where the rollers 3 are disengaged from the cylindrical surface 12 and the cam surface 11. It is. The cage 4 is restricted from moving in the axial direction by a step provided on the outer diameter surface of the cam ring 9 and a retaining ring 6 fitted to the outer diameter surface.

  The switch spring 5 has a configuration in which a pair of pressing pieces 5b are formed outward at both ends of a C-shaped ring portion 5a.

  As shown in FIGS. 1 and 3, the switch spring 5 is assembled so that the ring portion 5a is fitted into a spring accommodating recess 9a formed on the end face of the cam ring 9, and the pair of pressing pieces 5b are springs. Inserted into the notch 13 provided on the end surface of the retainer 4 from the notch portion 14 formed in the peripheral wall of the storage recess 9a, and the opposite end surfaces of the notch portion 14 and the notch 13 in the circumferential direction are opposite to each other. The roller 3 is held in the neutral position by the pressing.

  As shown in FIG. 1, the electromagnetic clutch 20 is fitted to the input shaft 1 so as to be slidable in the axial direction, and is opposed to the end face of the retainer 4 in the axial direction, and the armature 21 and the shaft. The rotor 22 is opposed in the direction, the electromagnet 23 is opposed to the rotor 22 in the axial direction, and the separation spring 24 is pressed in the direction in which the armature 21 is separated from the rotor 22.

  As shown in FIG. 2, the armature 21 is formed with an engagement hole 21a, and a protrusion 4a provided on the end surface of the retainer 4 is inserted into the engagement hole 21a, and the protrusion 4a and the engagement hole 21a are inserted. By the engagement, the armature 21 is prevented from rotating with respect to the retainer 4 and is movable in the axial direction.

  As shown in FIG. 1, the rotor 22 has cylindrical portions on the inner periphery and outer periphery, and the outer peripheral cylindrical portion is placed in a rotor guide 27 made of a non-magnetic material attached in the opening end portion of the outer ring 2. It is press-fitted and is prevented from rotating on the outer ring 2.

  The electromagnet 23 includes a field core 23a and an electromagnetic coil 23b supported by the field core 23a. The electromagnet 23 is disposed between the inner and outer cylindrical portions of the rotor 22, and the field core 23a can be supported non-rotatably on the housing (not shown).

  As shown in FIGS. 1 and 2, an engagement groove is formed in the inner peripheral portion of the rotor guide 27, and a retaining ring 25 for fixing the outer ring 2 is fitted in the engagement groove. Yes.

  A concave portion 32 that opens toward the armature 21 is formed at the axial end of the cam ring 9. The concave portion 32 has a shape opened to the inner diameter side edge and the outer diameter side edge of the axial end surface of the cam ring 9.

  A convex portion 31 is formed on the inner diameter portion of the armature 21 so as to protrude toward the inner diameter side. The convex portions 31 are provided in the same number as the concave portions 32, and the corresponding convex portions 31 and the concave portions 32 are arranged in the same direction around the axis so that the corresponding convex portions 31 can be fitted together in each concave portion 32. It has become.

The convex portion 31 is fitted into the concave portion 32 when the armature 21 is separated from the rotor 22 to the position where the armature 21 contacts the end face of the cam ring 9, and the armature 21 is prevented from rotating around the input shaft 1 by the fitting. (See FIG. 5).
Further, in a state where the armature 21 is attracted to the rotor 22, the convex portion 31 comes out of the concave portion 32 and releases the detent of the armature 21 (see FIG. 4).

  The rotation transmission device shown in this embodiment has these structures, and in a state where the energization of the electromagnet 23 to the electromagnetic coil 23b is interrupted, the roller 3 is held in a neutral state by the spring force of the switch spring 5, so that the input shaft 1 The rotation is not transmitted to the outer ring 2 and the input shaft 1 rotates idle.

  If the electromagnetic coil 23b of the electromagnet 23 is energized in the rotation state (driving state) of the input shaft 1, an attractive force is applied to the armature 21, and the armature 21 moves against the elasticity of the separation spring 24, and FIG. As shown to b), while being attracted | sucked by the rotor 22, the fitting with the convex part 31 and the recessed part 32 is cancelled | released.

  The frictional resistance acting on the attracting surfaces of the rotor 22 and the armature 21 becomes the rotational resistance of the cage 4, and the frictional resistance is set to a value larger than the spring force of the switch spring 5, so that the switch spring 5 is elastically deformed. Thus, the input shaft 1 and the cage 4 rotate relative to each other. By the relative rotation, the roller 3 is pushed into the narrow portion of the wedge-shaped space and engaged with the cylindrical surface 12 and the cam surface 11, and the rotation of the input shaft 1 is transmitted to the outer ring 2 through the roller 3.

  In the state of torque transmission from the input shaft 1 to the outer ring 2, when the energization to the electromagnetic coil 23b is cut off, the armature 21 is separated from the rotor 22 by the pressing of the separation spring 24, and as shown in FIG. It moves to a position where it abuts against the end face of 9.

  When the armature 21 is separated from the rotor 22, the retainer 4 is pushed by the spring force of the switch spring 5, the roller 3 is disengaged from the cylindrical surface 12 and the cam surface 11, and returned to the neutral position. For this reason, the rotation transmission from the input shaft 1 to the outer ring 2 is interrupted.

  In the idling state of the input shaft 1, the input shaft 1 and the cage 4 are elastically connected by the switch spring 5, so that the input shaft 1, the cage 4, and the roller 3 held by the cage 4 are both Rotate.

  For this reason, when the input shaft 1 idles, the roller 3 moves radially outward by centrifugal force and contacts the cylindrical surface 12, and drag torque is generated in the cage 4 due to frictional resistance acting on the contact portion. There is. This drag torque acts against the elastic holding force of the switch spring 5 and tries to rotate the cage 4 relative to the input shaft 1.

However, in a state where the armature 21 is separated, the convex portion 31 provided on the armature 21 is fitted into the concave portion 32 provided on the cam ring 9, and the armature 21 is prevented from rotating around the input shaft 1 by the fitting. The retainer 4 and the armature 21 are prevented from rotating by the engagement of the protruding piece 4a with the engagement hole 21a.
For this reason, if the convex part 31 fits into the concave part 32, the cage 4 will no longer rotate relative to the input shaft 1, and the two-way clutch 10 is misengaged when the input shaft 1 is idling. The inconvenience is not generated.

Further, if there is a rotational speed difference between the input shaft 1 and the armature 21 for a short time after the energization of the electromagnetic coil 23b is interrupted until the armature 21 is separated from the rotor 22 and contacts the end face of the cam ring 9. There is a problem that the convex portion 31 is difficult to smoothly fit into the concave portion 32.
This is because a difference in the rotational speed is generated, thereby causing a phase shift (direction around the axis with respect to the axis of the two-way clutch) between the concave portion 32 of the cam ring 9 and the convex portion 31 of the armature 21. .

Therefore, in a state where the convex portion 31 is fitted in the concave portion 32, a circumferential gap w is formed between the convex portion 31 and the concave portion 32 as shown in FIG. The size of the gap w is a numerical value obtained by subtracting the circumferential length of the convex portion 31 from the circumferential length of the concave portion 32 (the circumferential length around the axis of the two-way clutch 10), that is, This is the total value of the gap amounts w1 and w2 existing on both sides.
By interposing the gap w, even if there is a slight phase shift between the input shaft 1 and the armature 21, the convex portion 31 can be fitted into the concave portion 32 with the phase shifted.
Therefore, in particular, when the armature 21 first contacts the end surface of the cam ring 9 after being separated from the rotor 22 after the first contact, that is, the energization of the electromagnetic coil 23b is cut off, the convex portion 31 does not interfere with the concave portion 32. If the size is set so as to be fitted, the two-way clutch 10 can be smoothly shifted from the engaged state to the disengaged state without causing misengagement.

  In various types of rotation transmission devices of different types and uses, there are various accelerations and rotation speeds that can occur on the input shaft 1, or various transition times for the input shaft 1 and the outer ring 2 to transition from the engaged state to the idle state. It is.

For this reason, for example, the size of the gap w according to the acceleration of the input shaft 1, for example, the maximum acceleration of the input shaft 1 while the input shaft 1 and the outer ring 2 shift from the engaged state to the idle state. It is possible to adopt a method of setting
Further, for example, the size of the gap w depends on the rotational speed of the input shaft 1, for example, the maximum rotational speed of the input shaft 1 while the input shaft 1 and the outer ring 2 transition from the engaged state to the idling state. A method of setting the length can be adopted.
Further, a method of setting the size of the gap w according to the transition time, that is, the transition time from the engagement state of the input shaft 1 and the outer ring 2 to the idling state after the energization of the electromagnetic clutch 20 is released. Can be adopted.

  Assume that this rotation transmission device is applied to, for example, a motor rear wheel drive 4WD system.

The drive device connected to the input shaft 1 of the rotation transmission device is a motor, and the rotation of the rotation shaft (motor shaft) of the motor is transmitted to the input shaft 1. The outer ring 2 is connected to the drive shaft of the rear wheel.
Switching between 2WD and 4WD is possible by freeing the rotation transmission device during two-wheel drive (2WD) and locking the rotation transmission device during four-wheel drive.

In this configuration, it is assumed that the input shaft 1 is rotated by the driving force of the motor while the electromagnetic clutch 20 is energized, and the rotation is transmitted to the outer wheel 2 to drive the rear wheel.
During this traveling, it is assumed that the outer ring 2 rotates at a relatively higher speed than the input shaft 1 rotating by the driving force of the motor. As the outer ring 2 rotates at high speed, drag torque is generated on the input shaft 1 side.

If the energization of the electromagnetic coil 23b is interrupted in this state, the armature 21 and the cam ring 9 may be out of phase as they are. In this case, the motor is operated to make the input shaft 1 faster than the outer ring 2. The rotation speed is rotated in the same direction as the rotation direction of the outer ring 2 (a difference in rotational speed is generated between the input shaft 1 and the outer ring 2), and the phases of the convex portion 31 and the concave portion 32 are brought close to each other.
At this time, even if the input shaft 1 and the armature 21 are relatively rotated, the phase is shifted because the circumferential gap w of an appropriate size is interposed between the convex portion 31 and the concave portion 32. The convex part 31 can be fitted into the concave part 32 by the first contact in the state.

The gap w of the appropriate size means that when the armature 21 is separated from the rotor 22 and first hits the end surface of the cam ring 9 after the energization of the electromagnetic coil 23b is interrupted, the convex portion 31 does not interfere with the concave portion 32. It is the clearance gap w which has the circumferential direction width | variety which can be fitted.
That is, after the energization of the electromagnetic clutch 20 is released, the size of the gap w is set so that the convex portion 31 can be fitted into the concave portion 32 at the first contact.

In order to allow the convex portion 31 to be fitted into the concave portion 32 at the first contact, the size of the gap w depends on the maximum acceleration acting on the input shaft 1 during the phase alignment. Is set. If the maximum acceleration is large, the set gap w will be large accordingly.
As another configuration, the size of the gap w may be set according to the maximum number of rotations acting on the input shaft 1 and the transition time from the engaged state to the idle state after the energization is cut off. Good. If the maximum number of revolutions is large, the set gap w will be correspondingly large. In addition, if the transition time is long, the set gap w becomes large accordingly.

(Experimental example)
The difference in rotational speed that can occur between the input shaft 1 and the armature 21 is that the input shaft 1 is in a period from when the armature 21 is separated from the rotor 22 until the convex portion 31 and the concave portion 32 are fitted. If the maximum acceleration that can be generated is large, it tends to appear as a larger rotational speed difference. Also, when the maximum rotational speed is large, it tends to appear as a larger rotational speed difference.
For this reason, it is desirable to set the size of the gap w under the rotation condition of the input shaft 1 where the largest rotational speed difference can appear.

Therefore, the size of the circumferential gap w between the concave portion 32 of the cam ring 9 and the convex portion 31 of the armature 21 is variously changed, and the rotational speed of the input shaft 1 is fitted to each gap w at any time. An experiment was conducted to determine whether or not good or bad occurred.
In this experimental example, the load of the separation spring 24 was 15 (N) when the misengagement prevention mechanism was engaged, and the mass of the armature 21 was 100 (g).

The experimental results are shown in FIG. The vertical axis represents the rotational speed of the input shaft 1. The rotational speed during the experiment is the same as the rotational speed of the input shaft 1 until the convex portion 31 and the concave portion 32 are fitted after the energization of the electromagnetic clutch 20 is cut off. The maximum number of revolutions y (rpm) that can occur is assumed. The horizontal axis is the size c (mm) of the gap w to be set, and the circumferential length of the convex portion 31 from the circumferential length of the concave portion 32 (the circumferential length around the axis of the two-way clutch 10). The value obtained by subtracting the height, that is, the total value of the gap amounts w1 and w2 existing on both sides of the convex portion 31.
In the figure, when properly fitted, it is determined as “good” and “OK”. When it cannot be fitted, it is determined as “defective” and set to “NG”.

According to this experiment, the size of the gap w is larger than the maximum rotational speed y (rpm) allowed for the input shaft 1 when the convex portion 31 and the concave portion 32 are fitted.
x = y / 250
Assuming that the numerical value x obtained by the above equation is the lower limit value x (mm) and the size c (mm) of the gap w is determined to be a numerical value equal to or larger than the lower limit value x (mm), the occurrence of “NG” Is completely absent.

For this reason, the size c (mm) of the gap w is set to the maximum rotational speed y (rpm) allowed for the input shaft 1 when the convex portion 31 and the concave portion 32 are fitted.
x = y / 250
It is desirable that the numerical value of x obtained by the above formula be the lower limit value x (mm) and be determined to be a numerical value equal to or greater than the lower limit value x (mm).
From the experimental results, it is more preferable that the lower limit is 0.2 mm to 0.5 mm.

Further, if the size c (mm) of the gap w is too large, there is a possibility that the anti-rotation function between the input shaft 1 and the armature 21 may be hindered after the concave portion 32 is fitted to the convex portion 31.
For this reason, the angle of relative rotation around the axis allowed by the input shaft 1 and the armature 21 due to the gap w is such that the convex portion 31 is in the concave portion 32 as shown in FIG. The size c (mm) of the gap w is the upper limit, with numerical values of 5 to 9 (deg) on both sides in the circumferential direction at the neutral point located at the circumferential center of the convex portion 31 It is desirable to be determined so as to be a numerical value less than the value.
In the two-way clutch 10 used in this experimental example, the roller stroke in the circumferential direction between the neutral state and the engaged state of each roller 3 is set so that the roller stroke> the upper limit value.

A longitudinal front view showing an embodiment of a rotation transmission device according to the present invention FIG. 1 is an enlarged view of a built-in portion of the armature of FIG. Sectional view along the III-III line of FIG. 1 showing the idling state of the two-way clutch Fig. 2 shows the engaged state of the two-way clutch, where (a) is a cross-sectional view taken along line III-III in Fig. 1 and (b) is a cross-sectional view taken along line V-V in Fig. 1. (A) is sectional drawing which followed the VV line of FIG. 1, (b) is a principal part enlarged view of (a). Graph showing the relationship between input shaft speed and clearance

Explanation of symbols

1 Input shaft (input side member)
2 Outer ring (output side member)
3 Roller (engagement element)
4 Cage 5 Switch spring 9 Cam ring 10 Two-way clutch 11 Cam surface 12 Cylindrical surface 20 Electromagnetic clutch 21 Armature 22 Rotor 31 Convex part 32 Concave part

Claims (6)

Between the input side member (1, 9) and the output side member (2) provided on the outside thereof, the rotational torque is transmitted and cut off between the members (1, 9, 2). The two-way clutch (10) includes an electromagnetic clutch (20) that controls engagement and disengagement, and the two-way clutch (10) includes the input-side member ( 1) the retainer (4) assembled between the output side member (2), and the input by the relative rotation of the retainer (4) held by the retainer (4) with respect to the input side member (1). An engaging member (3) that is engaged between the opposing surfaces of the side member (1, 9) and the output side member (2) and couples the two members (1, 9, 2), and elastically deformed by the relative rotation. The cage (4) is in a neutral position where the engagement element (3) is disengaged by its restoring elasticity. The electromagnetic clutch (20) is slidable in the axial direction of the two-way clutch (10) with respect to the retainer (4), and the retainer (4). An armature (21) that is locked against rotation, a rotor (22) that is locked against the output side member (2) and faces the armature (21) in the axial direction, the rotor (22), and the rotor An electromagnet (23) that is opposed in the axial direction and attracts the armature (21) to the rotor (22) by energization, and a separation spring (24) that presses the armature (21) in a direction away from the rotor (22). And
One of the armature (21) and the input side member (9) is provided with a convex portion (31), and the other is provided with a concave portion (32). When the energization of the electromagnetic clutch (20) is released, the armature (21) is moved to the rotor. When separated from (22), the convex portion (31) is fitted into the concave portion (32), and the fitting prevents the armature (21) from rotating with respect to the input side member (9). In the rotation transmission device in which the vessel (4) is maintained in the neutral position,
When energization of the electromagnetic clutch (20) is released, the convex portion is formed after the armature (21) that is separated from the rotor (22) by the separation spring (24) contacts the input side member (9). When the phase of (31) and the concave portion (32) first matches, the gap (w) in which the convex portion (31) can be fitted into the concave portion (32) is the convex portion (31) and the concave portion ( 32) A rotation transmission device characterized by being provided between.   The rotation transmission according to claim 1, wherein a size (c (mm)) of the gap (w) is set according to an acceleration or a rotation speed of the input side member (1, 9). apparatus.   The size (c (mm)) of the gap (w) is set according to the acceleration of the input side member (1, 9), and the acceleration is engaged by the members (1, 9, 2). The rotation transmission device according to claim 2, characterized in that it is a maximum acceleration that can occur in the input side member (1, 9) during the transition from the state to the idling state.   The size of the gap (w) is set according to the number of rotations of the input side member (1, 9), and the number of rotations of the two members (1, 9, 2) is in an idle state from the engaged state. The rotation transmission device according to claim 2, wherein the rotation transmission device (1 (9)) is the maximum number of rotations (y (rpm)) that can occur in the input side member (1, 9) during the transition to step (3).   The size (c (mm)) of the gap (w) indicates the state of engagement between the input side members (1, 9) and the output side member (2) after the energization of the electromagnetic clutch (20) is released. The rotation transmission device according to claim 1, wherein the rotation transmission device is set according to a transition time from the idle state to the idle state. The size of the gap (w) is the maximum number of rotations allowed for the input side member (1, 9) while the both members (1, 9, 2) are shifted from the engaged state to the idle state ( y (rpm))
x = y / 250
The numerical value of x obtained by the above formula is determined as a lower limit value (x (mm)), and is determined to be a numerical value equal to or higher than the lower limit value (x (mm)),
Further, the angle of relative rotation around the axis allowed by the input side members (1, 9) and the armature (21) by the gap (w) is such that the convex portion (31) is in the concave portion (32). A numerical value that is 5 to 9 (deg) on both sides of the circumferential direction at the neutral point located in the circumferential center of the two-way clutch (10) is set as an upper limit value, and is determined to be a value equal to or lower than the upper limit value The rotation transmission device according to claim 4, wherein the rotation transmission device is provided.