JP2023156636A - rotation transmission device - Google Patents

Abstract

To provide a rotation transmission device for preventing a rotation phase between input/output shafts from being displaced by a prescribed angle or larger when being applied with torque, and preventing the occurrence of wobbling in a circumferential direction when locking a two-way clutch.SOLUTION: A rotation transmission device has: a first engagement part 37 provided on a member which rotates around a shaft together with one of an input shaft 5 or an output shaft 6 at an operation of a two-way clutch 2; and a second engagement part 38 provided on a member which rotates around a shaft together with the other of the input shaft 5 or the output shaft 6, wherein the first engagement part 37 and the second engagement part 38 are engaged with each other in a circumferential direction when the input shaft 5 and the output shaft 6 relatively rotate at the operation of the two-way clutch 2. The rotation transmission device has: an insertion hole 33 formed on a member in which the rotation around the shaft is prohibited at the operation of the two-way clutch 2; an engagement protrusion 34 formed on a member which rotates around the shaft together with the input shaft 5 or the output shaft 6, and inserted into the insertion hole 33; and an elastic member 46 for energizing the engagement protrusion 34 to the circumferential direction in the insertion hole 33.SELECTED DRAWING: Figure 1

Description

The present invention relates to a rotation transmission device that switches between transmitting and blocking rotation from an input shaft to an output shaft.

For example, as shown in Patent Document 1, a two-way clutch 10 and an electromagnetic clutch 20 housed in a housing 1 are used as main components of a rotation transmission device that switches transmission and cutoff of rotation from an input shaft to an output shaft. There is something I did.

The two-way clutch 10 includes an outer ring 3 having a cylindrical surface 11 formed on the inner periphery, and a flat cam surface 12 formed on the outer periphery in a continuous manner in the circumferential direction. It has a cam ring 4 (corresponding to the inner ring of the present application) that forms a wedge-shaped space. A roller 13 as an engager is installed between each cam surface 12 and the cylindrical surface 11. Each roller 13 is held by a pocket 15 formed in the holder 14. A cylindrical portion 16 is formed on the end surface of the cam ring 4, and a switch spring 17, which is partially cut away, is incorporated into the cylindrical portion 16. A pair of pressing pieces 17a are formed at both ends of the switch spring 17. This pressing piece 17a fits into a notch 19 provided at the end of the retainer 14 from a notch 18 formed in the cylindrical portion 16, and is opposed to the notch 18 and the notch 19 in the circumferential direction. A pair of side surfaces are pressed in opposite directions. This pressing elastically holds the retainer 14 in a position where the roller 13 is disengaged from the cylindrical surface 11 and the cam surface 12.

The electromagnetic clutch 20 includes an armature 21 (corresponding to the friction plate of the present application) arranged to face the open end surface of the outer ring 3, a switching plate 22 (corresponding to the armature of the present invention) arranged to face the armature 21, and a switching plate 22 (corresponding to the armature of the present application) arranged to face the armature 21. It has electromagnets 23 arranged to face each other, and a separation spring 24 provided between the electromagnets 23 and the switching plate 22. The open end surface of the outer ring 3 serves as a contact portion for the armature 21. The armature 21 is supported by the cam ring 4 so as to be freely movable in the axial direction. An engagement hole 26 is formed in the armature 21, and an engagement piece 27 formed at the open end of the retainer 14 is engaged with the engagement hole 26. Due to this engagement, the armature 21 is prevented from rotating relative to the retainer 14 and is movable in the axial direction. The switching plate 22 is fitted onto a first shaft 5 (corresponding to the input shaft of the present invention) connected to the cam ring 4, and is movable in the axial direction.

The electromagnet 23 has an electromagnetic coil 23a and a core 23b that supports the electromagnetic coil 23a. The core 23b has an outer cylinder part 23c and an inner cylinder part 23d, and an opening of an annular space formed between the outer cylinder part 23c and the inner cylinder part 23d faces the switching plate 22. A separation spring 24 is incorporated in the outer periphery of the end of the outer cylindrical portion 23c of the core 23b. This separation spring 24 urges the switching plate 22 in a direction away from the core 23b.

When the electromagnetic coil 23a of the electromagnet 23 is energized, the switching plate 22 is attracted to the end surfaces of the outer cylinder part 23c and the inner cylinder part 23d of the core 23b, and the coupling of the armature 21 to the outer ring 3 is released. Therefore, when the cam ring 4 rotates together with the first shaft 5 by steering the steering wheel, the rotation is transmitted to the retainer 14 via the switch spring 17. Then, the retainer 14 rotates together with the cam ring 4, and the roller 13 rotates while being held at a neutral position in which it is disengaged from the cylindrical surface 11 and the cam surface 12. Therefore, the rotation of the cam ring 4 is not transmitted to the outer ring 3, and the cam ring 4 (first shaft 5) rotates freely.

On the other hand, when the electromagnetic coil 23a is de-energized, the restoring elasticity of the separation spring 24 causes the switching plate 22 to move away from the core 23b. Then, due to this movement, the armature 21 is pressed against the contact portion 25 of the outer ring 3 and is coupled to the outer ring 3. Therefore, when the cam ring 4 rotates together with the first shaft 5 by steering the steering wheel, the cam ring 4 and the retainer 14 rotate relative to each other, and due to the relative rotation, the roller 13 engages with the cylindrical surface 11 and the cam surface 12. The two-way clutch 10 is now in a state where the cam ring 4 and the outer ring 3 are coupled. Therefore, the steering gear can be manually operated using the steering wheel (see paragraphs 0012 to 0029 and FIGS. 1 to 5 of Patent Document 1).

Japanese Patent Application Publication No. 2008-57625

In the rotation transmission device according to Patent Document 1, when the electromagnet is not energized, the armature 21 is pressed against the contact portion 25 of the outer ring 3 via the switching plate 22 due to the restoring elasticity of the separation spring 24, and the armature 21 and the outer ring are 3 is in a state of frictional contact. In this state, when the input shaft (cam ring 4) is rotated in both forward and reverse directions and a torque load is repeatedly applied between the input shaft (cam ring 4) and the output shaft (outer ring 3), elastic deformation occurs in the torque load portion of the roller clutch. Hysteresis may cause the rotational phase between the input and output shafts to gradually shift.

In addition, in this type of rotation transmission device, as shown in FIG. is prevented from rotating with respect to the retainer and is movable in the axial direction, but due to processing tolerances during press working, there is a gap between the circumferential inner surface of the insertion hole 61 and the engagement protrusion 62. There is a problem in that g is generated and rattling occurs in the circumferential direction when the two-way clutch is locked.

Therefore, the first object of this invention is to prevent the rotational phase between the input and output shafts from shifting by more than a predetermined angle when a torque load is applied between the input and output shafts while the two-way clutch is in a locked state. The second problem is to prevent rattling in the circumferential direction when the directional clutch is locked.

In order to solve the above first problem, in this invention,
A two-way clutch that switches between transmitting and interrupting rotation between the input shaft and the output shaft,
an electromagnetic clutch that brakes the two-way clutch;
A rotation transmission device comprising:
a first engaging portion provided on a member that rotates around an axis together with one of the input shaft or the output shaft when the two-way clutch is in operation;
a second engagement portion provided on a member that rotates around the axis together with the other of the input shaft or the output shaft;
and is configured such that the first engaging portion and the second engaging portion engage in a circumferential direction when the input shaft and the output shaft rotate relative to each other during operation of the two-way clutch. A rotation transmission device characterized by the following features has been constructed.

In this way, even if a torque load is applied between the input and output shafts and the rotational phase between the input and output shafts gradually shifts, the first engaging portion and the second engaging portion will engage in the circumferential direction, It is possible to prevent the rotational phase between the input and output shafts from shifting by more than a predetermined angle.

In the above configuration,
The two-way clutch is
an inner ring provided on one of the input shaft or the output shaft;
The shaft provided with the inner ring of the input shaft or the output shaft is an outer ring provided on the other shaft,
an engager disposed between the outer circumference of the inner ring and the inner circumference of the outer ring;
The engaging element is held and arranged so as to be movable in the circumferential direction between an engagement position where the engaging element is engaged with the outer periphery of the inner ring and an inner periphery of the outer ring, and a release position where the engagement is released. a retainer,
a centering spring that elastically holds the retainer in the released position and is prevented from rotating by the inner ring and the retainer so as to rotate together with the inner ring;
has
The electromagnetic clutch is
A field core having a C-shaped circumferential cross section, including a cylindrical inner cylinder part and an outer cylinder part having a larger diameter than the inner cylinder part, and a space between the inner cylinder part and the outer cylinder part of the field core. an electromagnet having a solenoid coil wound around the
an armature that is arranged to face the open end of the field core from the axial direction and is attracted to the field core when the electromagnet is excited;
a friction plate arranged to be movable in the axial direction while being prevented from rotating with respect to the retainer;
a separation spring that urges the armature toward the friction plate;
has
The second engaging portion is provided at the axial end of the outer ring facing the friction plate, and the second engaging portion engages the friction plate when the friction plate is pressed against the outer ring by the urging force of the separation spring. It is preferable that the first engaging portions are respectively formed so as to be engageable with the first engaging portions in the circumferential direction.

In this way, both the engaging parts engage between the outer ring and the friction plate, which are provided adjacent to each other in the axial direction, so that the effect of preventing rotational phase shift between the input and output shafts is effectively exerted. .

In each of the above configurations,
The first engaging portion is a protrusion extending outward from the outer edge of the friction plate, and the second engaging portion is a protrusion extending outward from the outer circumferential surface of the outer ring. At least one of the first engaging portion and the second engaging portion is bent in the axial direction so that the first engaging portion and the second engaging portion can be engaged in the circumferential direction. is preferable.

In this way, the anti-rotation effect due to the engagement between the first engaging portion and the second engaging portion can be reliably exerted without affecting the frictional contact between the friction plate and the outer ring.

In each of the above configurations,
The first engaging portion and the second engaging portion are formed at equal intervals in the circumferential direction, and the numbers of the first engaging portion and the second engaging portion are different. It is preferable to do so.

In this way, when the rotational phase between the input and output shafts gradually shifts, the first engagement part and the second engagement part can be engaged at a smaller relative rotation angle, and the The rotational phase shift can be suppressed as much as possible.

In each of the above configurations,
It is preferable that the inner ring is provided with a biasing member that biases the friction plate in a direction toward the armature.

In this way, when the electromagnet is energized and the armature is attracted, the friction plate can be moved toward the armature by the biasing force of the biasing member, and the first engaging portion formed on the friction plate and the outer ring are connected to each other. It is possible to reliably prevent the formed second engaging portion from unintentionally engaging in the circumferential direction and preventing rotation of the retainer.

In each of the above configurations,
An insertion hole is formed in the friction plate, and an engagement protrusion that is inserted into the insertion hole is formed at the axial end of the retainer, and the engagement protrusion is attached to the insertion hole in the circumferential direction. It is preferable that an elastic member is provided to apply pressure.

In this way, no gap is created in the circumferential direction between the inner surface of the insertion hole and the engagement protrusion, so that it is possible to prevent rattling in the circumferential direction when the two-way clutch is locked.

In each of the above configurations,
The elastic member is provided inside a fixing portion fixed to the friction plate and the insertion hole, and urges the engagement protrusion inserted into the insertion hole toward the circumferential center of the insertion hole. It is preferable to have a configuration including an elastic portion.

In this way, even when the input shaft is rotated in either the forward or reverse direction, a biasing force is applied from the elastic portion toward the center in the circumferential direction, so that a comfortable operating feeling can be obtained.

Moreover, in order to solve the above second problem, in this invention,
A two-way clutch that switches between transmitting and interrupting rotation between the input shaft and the output shaft,
an electromagnetic clutch that brakes the two-way clutch;
A rotation transmission device comprising:
an insertion hole formed in a member that prevents rotation around an axis during operation of the two-way clutch;
an engagement protrusion formed on a member that rotates around the axis together with the input shaft or the output shaft and inserted into the insertion hole;
an elastic member that biases the engagement protrusion in the circumferential direction within the insertion hole;
A rotation transmission device is constructed, which is characterized by having the following.

In this way, no gap is created in the circumferential direction between the inner surface of the insertion hole and the engagement protrusion, so that it is possible to prevent rattling in the circumferential direction when the two-way clutch is locked.

In the above configuration,
The two-way clutch is
an inner ring provided on one of the input shaft or the output shaft;
The shaft provided with the inner ring of the input shaft or the output shaft is an outer ring provided on the other shaft,
an engager disposed between the outer circumference of the inner ring and the inner circumference of the outer ring;
The engaging element is held and arranged so as to be movable in the circumferential direction between an engagement position where the engaging element is engaged with the outer periphery of the inner ring and an inner periphery of the outer ring, and a release position where the engagement is released. a retainer,
a centering spring that elastically holds the retainer in the released position and is prevented from rotating by the inner ring and the retainer so as to rotate together with the inner ring;
has
The electromagnetic clutch is
A field core having a C-shaped circumferential cross section, including a cylindrical inner cylinder part and an outer cylinder part having a larger diameter than the inner cylinder part, and a space between the inner cylinder part and the outer cylinder part of the field core. an electromagnet having a solenoid coil wound around the
an armature that is arranged to face the open end of the field core from the axial direction and is attracted to the field core when the electromagnet is excited;
a friction plate arranged to be movable in the axial direction while being prevented from rotating with respect to the retainer;
a separation spring that urges the armature toward the friction plate;
has
Preferably, the insertion hole is formed in the friction plate, the engagement protrusion is formed at an axial end of the retainer, and the elastic member is provided in the insertion hole. .

In this case, it is only necessary to add an elastic member to the existing two-way clutch configuration, so that the rattling prevention effect can be obtained simply and at low cost.

In each of the above configurations,
The elastic member is provided inside a fixing portion fixed to the friction plate and the insertion hole, and urges the engagement protrusion inserted into the insertion hole toward the circumferential center of the insertion hole. It is preferable to have a configuration including an elastic portion.

In this way, even when the input shaft is rotated in either the forward or reverse direction, a biasing force is applied from the elastic portion toward the center in the circumferential direction, so that a comfortable operating feeling can be obtained.

In each of the above configurations,
It is preferable that the clutch be used as a clutch for connecting both shafts on the input shaft side and the output shaft side when the steer-by-wire device fails.

In this way, when an electromagnet or the like fails, it is possible to quickly shift to manual operation, thereby ensuring operability and safety.

The rotation transmission device according to the present invention includes a first engaging portion provided on a member that rotates around the shaft together with one of the input shaft or the output shaft, and a first engaging portion provided on the member that rotates around the shaft together with the other of the input shaft or the output shaft when the two-way clutch is operated. a second engaging part provided on a member that rotates around the shaft, and when the input shaft and the output shaft rotate relative to each other during operation of the two-way clutch, the first engaging part and the second engaging part are configured so that they engage in the circumferential direction, so even if a torque load is applied between the input and output shafts and the rotational phase between the input and output shafts gradually shifts, the first engagement part and the second engagement part will By engaging in the circumferential direction, it is possible to prevent the rotational phase between the input and output shafts from shifting by more than a predetermined angle.

Further, the rotation transmission device according to the present invention includes an insertion hole formed in a member that is prevented from rotating around the shaft when the two-way clutch is operated, and a member that rotates around the shaft together with the input shaft or the output shaft, Since the configuration includes an engaging protrusion that is inserted into the insertion hole and an elastic member that biases the engaging protrusion in the circumferential direction within the insertion hole, there is a gap between the inner surface of the insertion hole and the engaging protrusion in the circumferential direction. This prevents a gap from occurring and prevents rattling in the circumferential direction when the two-way clutch is locked.

A sectional view showing a first embodiment of a rotation transmission device according to the present invention A sectional view of the main parts of the rotation transmission device shown in Figure 1 Cross-sectional view along line III-III in Figure 1 Cross-sectional view along line IV-IV in Figure 1 Cross-sectional view of the main parts showing the adsorption state of the armature Cross-sectional view of main parts showing armature in non-adsorption state A configuration diagram of a steer-by-wire device that employs the rotation transmission device shown in Figure 1. A sectional view showing a second embodiment of the rotation transmission device according to the present invention A sectional view of the main parts of the rotation transmission device shown in FIG. Cross-sectional view along line XX in Figure 8 An exploded perspective view of the main parts of the rotation transmission device shown in FIG. A sectional view of the main parts of the rotation transmission device shown in FIG. Cross-sectional view along line XIII-XIII in Figure 12 A sectional view showing a third embodiment of the rotation transmission device according to the present invention Cross-sectional view along the XV-XV line in Figure 14 Diagram showing the main parts of a general rotation transmission device

A first embodiment of a rotation transmission device 1 according to the present invention will be described using FIGS. 1 to 6. This rotation transmission device 1 includes a two-way clutch 2 and an electromagnetic clutch 3, as shown in FIG. Internal parts such as the two-way clutch 2 are housed inside the case 4.

The two-way clutch 2 has a function of switching transmission and interruption of rotation between the input shaft 5 and the output shaft 6. The two-way clutch 2 includes an inner ring 8 integrally formed at the end of an input shaft 5 connected to a steering wheel 7 (see FIG. 7), etc., and an inner ring 8 formed integrally with the input shaft 5, and a shaft end of an output shaft 6. An outer ring 9 integrally constructed with the output shaft 6, an engager 10 disposed between the outer periphery of the inner ring 8 and the inner periphery of the outer ring 9, a retainer 11 holding the engager 10, and a centering spring. 12.

A plurality of cam surfaces 13 are formed on the outer peripheral surface of the inner ring 8 at equal intervals in the circumferential direction. In this embodiment, the cam surfaces 13 are formed at eight locations, but the number may be changed as appropriate. A cylindrical surface 14 is formed on the inner peripheral surface of the outer ring 9. Between the inner ring 8 and the outer ring 9, a roller serving as an engaging element 10 (hereinafter, the same reference numeral as the engaging element 10 is attached) is arranged so as to face each cam surface 13. Each roller 10 is held by a holder 11.

The retainer 11 is a cylindrical member in which a flange 15 extending radially inward is formed at one end in the axial direction. Pockets 16 are formed on the cylindrical surface at equal intervals in the circumferential direction, and each roller 10 is held rotatably within the pockets 16. A retaining ring 17 is provided on the flange 15 so as to be hooked onto the stepped portion of the inner ring 8, and restricts the axial movement of the retainer 11.

A wedge space is formed between each cam surface 13 and the cylindrical surface 14, in which the radial gap between the cam surface 13 and the cylindrical surface 14 becomes narrower on both sides than at the center in the circumferential direction. . The radial gap at the center is wider than the diameter of the roller 10, and on both sides of the center the radial gap is narrower than the diameter of the roller 10. The retainer 11 has two positions: an engagement position where the roller 10 engages with a cam surface 13 formed on the outer periphery of the inner ring 8 and a cylindrical surface 14 formed on the inner periphery of the outer ring 9, and a release position where this engagement is released. It is possible to move in the circumferential direction between.

The centering spring 12 is an elastic member that is prevented from rotating by the inner ring 8 and the holder 11 so as to elastically hold the holder 11 in the released position and rotate together with the inner ring 8. The centering spring 12 includes a C-shaped annular portion 18 made of steel wire wound in a C-shape, and a pair of extension portions 19 extending radially outward from both ends of the C-shaped annular portion 18, respectively.

A recess 20 and a radial groove 21 for holding the centering spring 12 are formed in the axial end surface of the inner ring 8 . The recess 20 is an arcuate groove extending along the circumferential direction. The radial groove 21 extends radially outward from the recess 20 to the outer circumference of the inner ring 8 . Furthermore, a concave cage groove 22 is formed at the axial end of the cage 11 . The radial groove 21 and the cage groove 22 have the same circumferential width. The C-shaped annular portion 18 of the centering spring 12 is fitted into the recess 20. Further, the pair of extensions 19 are inserted into a radial groove 21 formed in the inner ring 8 and a cage groove 22 formed in the cage 11.

The extending portion 19 is in contact with the groove inner surface at both circumferential ends of the radial groove 21 and the groove inner surface at both circumferential ends of the retainer groove 22 . As a result, the centering spring 12 is prevented from rotating by the inner ring 8 so as to rotate together with the inner ring 8, and is also prevented from rotating by the retainer 11, and acts on the contact portion between the extending portion 19 and the retainer groove 22. The retainer 11 can be elastically held in the released position by the circumferential force exerted thereon.

The electromagnetic clutch 3 has a function of braking the two-way clutch 2, and includes an electromagnet 23, an armature 24, a friction plate 25, and a separation spring 26.

The electromagnet 23 includes a field core 29 having a C-shaped circumferential cross section, which includes a cylindrical inner cylinder part 27 and an outer cylinder part 28 having a larger diameter than the inner cylinder part 27, and an inner cylinder part 27 of the field core 29. It has a solenoid coil 30 wound between the outer cylinder parts 28.

The armature 24 is a disc-shaped member made of a magnetic material and has a through hole formed in the center. The armature 24 is arranged so as to face the open end of the field core 29 from the axial direction. An annular projection 31 is formed on the surface of the armature 24 facing the friction plate 25. The annular protrusion 31 is configured to bias the vicinity of the outer peripheral edge of the friction plate 25. The radial position of this annular protrusion 31 corresponds to the radial position of a friction surface portion 32 formed on the axial end surface of the outer ring 9, which generates frictional resistance by contacting the friction plate 25.

The friction plate 25 is a disc-shaped member made of a non-magnetic material and has a through hole formed in the center. Insertion holes 33 are formed at two locations in the circumferential direction on the plate surface. At the axial end of the retainer 11, engaging protrusions 34 that are inserted into the insertion holes 33 are formed at two locations in the circumferential direction. By inserting the engagement protrusion 34 into the insertion hole 33 from the axial direction, the friction plate 25 becomes movable in the axial direction while being prevented from rotating relative to the retainer 11. Further, the friction plate 25 is provided so as to close the recess 20 formed in the inner ring 8, and also functions as a member for preventing the centering spring 12 provided in the recess 20 from coming off.

The inner ring 8 is provided with a biasing member 35 that biases the friction plate 25 in the direction toward the armature 24 . As this biasing member 35, an annular spring such as a wave washer can be employed. A retaining ring 36 is provided on the inner peripheral edge of the friction plate 25 facing the armature 24. As a result, the friction plate 25 can only move in the axial direction within the range of the position where one surface abuts the friction surface portion 32 formed on the outer ring 9 and the position where the other surface abuts the retaining ring 36. Permissible.

Five first engaging portions 37 are formed on the friction plate 25 at equal intervals (72 degree pitch) in the circumferential direction of the friction plate 25 . The first engaging portion 37 is a projection extending outward from the outer edge of the friction plate 25 , and its end portion is bent in the axial direction toward the outer ring 9 . Furthermore, four second engaging portions 38 are formed at equal intervals (90 degree pitch) in the circumferential direction of the outer ring 9 at the axial end portion facing the friction plate 25 of the outer ring 9 . The second engaging portion 38 is a projection extending outward from the outer circumferential surface of the outer ring 9 . The axial position of the axially bent tip of the first engaging part 37 overlaps with the axial position of the second engaging part 38 when the friction plate 25 is pressed against the outer ring by the urging force of the separation spring 26. When the outer ring 9 and the friction plate 25 rotate relative to each other around the axis, the first engaging portion 37 and the second engaging portion 38 can engage in the circumferential direction. The axial position of the retaining ring 36 is set to such a position that the first engaging part 37 and the second engaging part 38 do not overlap in the axial direction when the friction plate 25 is in contact with the retaining ring 36. .

Note that instead of bending the end of the first engaging portion 37 in the axial direction toward the outer ring 9, the end of the second engaging portion 38 may be bent in the axial direction toward the friction plate 25. In some cases it is possible. Further, there are cases in which the ends of the first engaging part 37 can be bent in the axial direction so as to face the outer ring 9, and the ends of the second engaging part 38 can be bent in the axial direction so as to face the friction plate 25. be.

A separation spring 26 is provided between the end of the field core 29 (inner cylindrical portion 27) and the armature 24 to bias the armature 24 toward the friction plate 25. As this separation spring 26, an annular spring such as a wave washer can be adopted.

The case 4 is a cup-shaped member made of a non-magnetic material, and internal parts such as the two-way clutch 2 and the electromagnetic clutch 3 are housed inside the case 4, and an input shaft 5 and an output shaft 6 are arranged around the axis. It is inserted. An elastic member 39 that presses the two-way clutch 2 and the electromagnetic clutch 3 in the axial direction (in this embodiment, toward the input shaft 5 side) is provided inside the case 4 on the output shaft 6 side. As the elastic member 39, in addition to an annular spring such as a wave washer, coil springs provided at a plurality of locations in the circumferential direction, etc. can be employed.

Bearings 40, 41, and 42 are provided between the input shaft 5 (inner ring 8) and case 4, between the inner ring 8 and outer ring 9, and between the output shaft 6 (outer ring 9) and case 4, respectively. It is possible to rotate relative to each other around the axis. Retaining rings 43 and 44 are provided at the input shaft side end of the case 4 to prevent the bearing 40 and field core 29 provided between the input shaft 5 and the case 4 from slipping out of the case 4. .

The operation of this rotation transmission device 1 will be explained. When the solenoid coil 30 is energized, the armature 24 is attracted to the field core 29 against the urging force of the separation spring 26, as shown in FIG. When the armature 24 is in the attracted state, no pressing force is applied from the armature 24 to the friction plate 25, so the friction plate 25 is displaced in the axial direction by the urging force of the urging member 35 until it comes into contact with the retaining ring 36. At this time, gaps are created in the axial direction between the armature 24 and the friction plate 25 and between the first engagement part 37 and the second engagement part 38, so that the friction plate 25 and the friction surface part 32 do not come into frictional contact. Therefore, the outer ring 9 and the retainer 11 can rotate relative to each other around the axis. Then, the retainer 11 is rotated by the centering spring 12, which rotates together with the inner ring 8, and is held at the released position by the elastic restoring force of the centering spring 12. Therefore, the roller 10 held by the retainer 11 does not engage with the cam surface 13 on the outer periphery of the inner ring 8 and the cylindrical surface 14 on the inner periphery of the outer ring 9, and the input shaft 5 (inner ring 8) ), it can freely rotate in either the forward or reverse direction.

On the other hand, when the solenoid coil 30 is de-energized, the attraction of the armature 24 to the inner cylinder part 27 and the outer cylinder part 28 is released, as shown in FIG. In the non-adsorption state of the armature 24, the armature 24 urged by the separation spring 26 presses the friction plate 25 against the urging force of the urging member 35, and the friction plate 25 and the outer ring against which this friction plate 25 is pressed. The friction surface portions 32 of No. 9 come into frictional contact. At this time, when the input shaft 5 (inner ring 8) rotates in either the forward or reverse direction, the rotational force of the input shaft 5 (inner ring 8) is transmitted to the retainer 11 from the centering spring 12 that rotates together with the input shaft 5 (inner ring 8). However, since the braking force due to the frictional contact between the friction plate 25 which is prevented from rotating by the retainer 11 and the friction surface portion 32 acts on the retainer 11 via the friction plate 25, the input shaft 5 (inner ring 8) rotates relative to each other. As a result, the retainer 11 that moves in the circumferential direction with respect to the inner ring 8 pushes one of the pair of extensions 19 of the centering spring 12 in the circumferential direction on the inner surface of the retainer groove 22 to elastically bend it. It moves in the circumferential direction from the release position toward the engagement position against the centering spring 12. When this circumferential movement reaches a predetermined angular amount, the retainer 11 reaches the engagement position, and the input shaft 5 (inner ring 8) and output shaft 6 (outer ring 9) rotate together.

In this embodiment, when the friction plate 25 is pressed against the outer ring 9, the first engagement part 37 formed on the friction plate 25 and the second engagement part 38 formed on the outer ring 9 engage in the circumferential direction. Therefore, even if a torque load is applied between the input and output shafts 5 and 6 and the rotational phase between the input and output shafts 5 and 6 gradually deviates, the first engaging portion 37 can be connected to the second engaging portion 38. This can prevent the rotational phase between the input and output shafts 5 and 6 from shifting by more than a predetermined angle.

In addition, in this embodiment, an elastic member 39 is provided inside the case 4 to pressurize internal parts such as the two-way clutch 2 and the electromagnetic clutch 3 in the axial direction, so that axial wobbling of the internal parts is prevented. The number of retaining rings to prevent this can be minimized.

Furthermore, in this embodiment, since the input shaft 5 and the inner ring 8 are integrally configured, it is possible to prevent the input shaft 5 from wobbling in the circumferential direction due to the rotation of the inner ring 8.

Furthermore, in this embodiment, since the case 4 and the friction plate 25 are made of non-magnetic material, the magnetic force of the electromagnet 23 is less likely to leak to the outside of the case 4. Therefore, sufficient adsorption force of the armature 24 by the electromagnet 23 can be ensured.

This rotation transmission device 1 can be used, for example, as a clutch in a steer-by-wire device of a vehicle, as shown in FIG. Normally, the electromagnet 23 is energized so that the steering wheel 7 side (input shaft 5 side) and the steering device 45 side (output shaft 6 side) are not directly connected mechanically. By connecting both shafts on the input shaft 5 side and the output shaft 6 side in the event of a failure, it is possible to mechanically perform a steering operation using the steering wheel 7. In this way, it is possible to quickly shift to manual operation in the event of a failure, so it is possible to ensure the operability and safety of the vehicle.

A second embodiment of the rotation transmission device 1 according to the present invention will be described using FIGS. 8 to 13. This rotation transmission device includes a two-way clutch 2 and an electromagnetic clutch 3, as shown in FIG. Internal parts such as the two-way clutch 2 are housed inside the case 4.

The two-way clutch 2 has a function of switching transmission and interruption of rotation between the input shaft 5 and the output shaft 6. The two-way clutch 2 includes an inner ring 8 integrally formed at the end of an input shaft 5 connected to a steering wheel 7 (see FIG. 7), etc., and an inner ring 8 formed integrally with the input shaft 5, and a shaft end of an output shaft 6. An outer ring 9 integrally constructed with the output shaft 6, an engager 10 disposed between the outer periphery of the inner ring 8 and the inner periphery of the outer ring 9, a retainer 11 holding the engager 10, and a centering spring. 12.

A plurality of cam surfaces 13 are formed on the outer peripheral surface of the inner ring 8 at equal intervals in the circumferential direction. In this embodiment, the cam surfaces 13 are formed at eight locations, but the number may be changed as appropriate. A cylindrical surface 14 is formed on the inner peripheral surface of the outer ring 9. Between the inner ring 8 and the outer ring 9, a roller serving as an engaging element 10 (hereinafter, the same reference numeral as the engaging element 10 is attached) is arranged so as to face each cam surface 13. Each roller 10 is held by a holder 11.

The retainer 11 is a cylindrical member in which a flange 15 extending radially inward is formed at one end in the axial direction. Pockets 16 are formed on the cylindrical surface at equal intervals in the circumferential direction, and each roller 10 is held rotatably within the pockets 16. A retaining ring 17 is provided on the flange 15 so as to be hooked onto the stepped portion of the inner ring 8, and restricts the axial movement of the retainer 11.

A wedge space is formed between each cam surface 13 and the cylindrical surface 14, in which the radial gap between the cam surface 13 and the cylindrical surface 14 becomes narrower on both sides than at the center in the circumferential direction. . The radial gap at the center is wider than the diameter of the roller 10, and on both sides of the center the radial gap is narrower than the diameter of the roller 10. The retainer 11 has two positions: an engagement position where the roller 10 engages with a cam surface 13 formed on the outer periphery of the inner ring 8 and a cylindrical surface 14 formed on the inner periphery of the outer ring 9, and a release position where this engagement is released. It is possible to move in the circumferential direction between.

The centering spring 12 is an elastic member that is prevented from rotating by the inner ring 8 and the holder 11 so as to elastically hold the holder 11 in the released position and rotate together with the inner ring 8. The centering spring 12 includes a C-shaped annular portion 18 made of steel wire wound in a C-shape, and a pair of extension portions 19 extending radially outward from both ends of the C-shaped annular portion 18, respectively.

A recess 20 and a radial groove 21 for holding the centering spring 12 are formed in the axial end surface of the inner ring 8 . The recess 20 is an arcuate groove extending along the circumferential direction. The radial groove 21 extends radially outward from the recess 20 to the outer circumference of the inner ring 8 . Furthermore, a concave cage groove 22 is formed at the axial end of the cage 11 . The radial groove 21 and the cage groove 22 have the same circumferential width. The C-shaped annular portion 18 of the centering spring 12 is fitted into the recess 20. Further, the pair of extensions 19 are inserted into a radial groove 21 formed in the inner ring 8 and a cage groove 22 formed in the cage 11.

The extending portion 19 is in contact with the groove inner surface at both circumferential ends of the radial groove 21 and the groove inner surface at both circumferential ends of the retainer groove 22 . As a result, the centering spring 12 is prevented from rotating by the inner ring 8 so as to rotate together with the inner ring 8, and is also prevented from rotating by the retainer 11, and acts on the contact portion between the extending portion 19 and the retainer groove 22. The retainer 11 can be elastically held in the released position by the circumferential force exerted thereon.

The electromagnetic clutch 3 has a function of braking the two-way clutch 2, and includes an electromagnet 23, an armature 24, a friction plate 25, and a separation spring 26.

The electromagnet 23 includes a field core 29 having a C-shaped circumferential cross section, which includes a cylindrical inner cylinder part 27 and an outer cylinder part 28 having a larger diameter than the inner cylinder part 27, and an inner cylinder part 27 of the field core 29. It has a solenoid coil 30 wound between the outer cylinder parts 28.

The armature 24 is a disc-shaped member made of a magnetic material and has a through hole formed in the center. The armature 24 is arranged so as to face the open end of the field core 29 from the axial direction. An annular projection 31 is formed on the surface of the armature 24 facing the friction plate 25. The annular protrusion 31 is configured to bias the vicinity of the outer peripheral edge of the friction plate 25. The radial position of this annular protrusion 31 corresponds to the radial position of a friction surface portion 32 formed on the axial end surface of the outer ring 9, which generates frictional resistance by contacting the friction plate 25.

The friction plate 25 is a disc-shaped member made of a non-magnetic material and has a through hole formed in the center. Insertion holes 33 are formed at two locations in the circumferential direction on the plate surface. At the axial end of the retainer 11, engaging protrusions 34 that are inserted into the insertion holes 33 are formed at two locations in the circumferential direction. By inserting the engagement protrusion 34 into the insertion hole 33 from the axial direction, the friction plate 25 becomes movable in the axial direction while being prevented from rotating relative to the retainer 11. Further, the friction plate 25 is provided so as to close the recess 20 formed in the inner ring 8, and also functions as a member for preventing the centering spring 12 provided in the recess 20 from coming off.

As shown in FIGS. 11 to 13, the insertion hole 33 is provided with an elastic member 46 that biases the engagement protrusion 34 in the circumferential direction. The elastic member 46 includes a fixing portion 47 fixed to the friction plate 25 and an engaging protrusion 34 provided inside the insertion hole 33 so as to move the engagement protrusion 34 inserted into the insertion hole 33 toward the circumferential center of the insertion hole 33. It has an elastic part 48 that urges. The fixing part 47 has a pair of opposing claws, and is attached so that the pair of claws straddles between the insertion hole 33 and the through hole 49 formed at the center of the friction plate 25 for passing the shaft therethrough. . The elastic portion 48 is elastic and has a pair of opposing claws. In a natural state where no external force is applied, the size of the gap between the pair of claws is narrower than the circumferential width of the engagement protrusion 34 inserted into the insertion hole 33. That is, when the engagement protrusion 34 is inserted into the insertion hole 33, the elastic portion 48 is elastically deformed and urges the engagement protrusion 34 from both circumferential sides toward the circumferential center (as indicated by the arrow in FIG. 13). reference).

A retaining ring 36 is provided on the inner peripheral edge of the friction plate 25 facing the armature 24. This retaining ring 6 restricts the movement of the friction plate 25 in the axial direction.

A separation spring 26 is provided between the end of the field core 29 (inner cylindrical portion 27) and the armature 24 to bias the armature 24 toward the friction plate 25. As this separation spring 26, an annular spring such as a wave washer can be adopted.

The case 4 is a cup-shaped member made of a non-magnetic material, and internal parts such as the two-way clutch 2 and the electromagnetic clutch 3 are housed inside the case 4, and an input shaft 5 and an output shaft 6 are arranged around the axis. It is inserted. An elastic member 36 that presses the two-way clutch 2 and the electromagnetic clutch 3 in the axial direction (in this embodiment, toward the input shaft 5 side) is provided inside the case 4 on the output shaft 6 side. As the elastic member 36, in addition to an annular spring such as a wave washer, coil springs provided at a plurality of locations in the circumferential direction can be used.

Bearings 40, 41, and 42 are provided between the input shaft 5 (inner ring 8) and case 4, between the inner ring 8 and outer ring 9, and between the output shaft 6 (outer ring 9) and case 4, respectively. It is possible to rotate relative to each other around the axis. Retaining rings 43 and 44 are provided at the input shaft side end of the case 4 to prevent the bearing 40 and field core 29 provided between the input shaft 5 and the case 4 from slipping out of the case 4. .

The operation of this rotation transmission device 1 will be explained. When the solenoid coil 30 is energized, the armature 24 is attracted to the field core 29 against the urging force of the separation spring 26 . In the adsorbed state of the armature 24, no pressing force is applied from the armature 24 to the friction plate 25, so the friction plate 25 and the friction surface portion 32 do not come into frictional contact, and the outer ring 9 and the retainer 11 can rotate relative to each other around the shaft. . Then, the retainer 11 is rotated by the centering spring 12, which rotates together with the inner ring 8, and is held at the released position by the elastic restoring force of the centering spring 12. Therefore, the roller 10 held by the retainer 11 does not engage with the cam surface 13 on the outer periphery of the inner ring 8 and the cylindrical surface 14 on the inner periphery of the outer ring 9, and the input shaft 5 (inner ring 8) ), it can freely rotate in either the forward or reverse direction.

On the other hand, when the solenoid coil 30 is de-energized, the adsorption of the armature 24 to the inner cylinder part 27 and the outer cylinder part 28 is released. In the non-adsorption state of the armature 24, the armature 24 urged by the separation spring 26 presses the friction plate 25, and the friction plate 25 and the friction surface portion 32 of the outer ring 9 against which the friction plate 25 is pressed come into frictional contact. . At this time, when the input shaft 5 (inner ring 8) rotates in either the forward or reverse direction, the rotational force of the input shaft 5 (inner ring 8) is transmitted to the retainer 11 from the centering spring 12 that rotates together with the input shaft 5 (inner ring 8). However, since the braking force due to the frictional contact between the friction plate 25 which is prevented from rotating by the retainer 11 and the friction surface portion 32 acts on the retainer 11 via the friction plate 25, the input shaft 5 (inner ring 8) rotates relative to each other. As a result, the retainer 11 that moves in the circumferential direction with respect to the inner ring 8 pushes one of the pair of extensions 19 of the centering spring 12 in the circumferential direction on the inner surface of the retainer groove 22 to elastically bend it. It moves in the circumferential direction from the release position toward the engagement position against the centering spring 12. When this circumferential movement reaches a predetermined angular amount, the retainer 11 reaches the engagement position, and the input shaft 5 (inner ring 8) and output shaft 6 (outer ring 9) rotate together.

In this embodiment, by providing the elastic member 46, there is no gap in the circumferential direction between the inner surface of the insertion hole 33 and the engagement protrusion 34 (see FIGS. 12 and 13), so that the two-way clutch 2 It is possible to prevent wobbling in the circumferential direction when locked.

In addition, in this embodiment, an elastic member 39 is provided inside the case 4 to pressurize internal parts such as the two-way clutch 2 and the electromagnetic clutch 3 in the axial direction, so that axial wobbling of the internal parts is prevented. The number of retaining rings to prevent this can be minimized.

Furthermore, in this embodiment, since the input shaft 5 and the inner ring 8 are integrally configured, it is possible to prevent the input shaft 5 from wobbling in the circumferential direction due to the rotation of the inner ring 8.

Furthermore, in this embodiment, since the case 4 and the friction plate 25 are made of non-magnetic material, the magnetic force of the electromagnet 23 is less likely to leak to the outside of the case 4. Therefore, sufficient adsorption force of the armature 24 by the electromagnet 23 can be ensured.

A third embodiment of the rotation transmission device 1 according to the present invention will be described using FIGS. 14 and 15. This rotation transmission device 1 has the same basic configuration as the rotation transmission device 1 according to the first embodiment, except that an elastic member 46 is provided in the insertion hole 33 to bias the engagement protrusion 34 in the circumferential direction. They are different.

As shown in FIGS. 11 to 13, the elastic member 46 includes a fixing portion 47 fixed to the friction plate 25 and an engaging protrusion 34 provided inside the insertion hole 33. It has an elastic portion 48 that urges toward the circumferential center of the insertion hole 33. The fixing part 47 has a pair of opposing claws, and is attached so that the pair of claws straddles between the insertion hole 33 and the through hole 49 formed at the center of the friction plate 25 for passing the shaft therethrough. . The elastic portion 48 is elastic and has a pair of opposing claws. In a natural state where no external force is applied, the size of the gap between the pair of claws is narrower than the circumferential width of the engagement protrusion 34 inserted into the insertion hole 33. That is, when the engagement protrusion 34 is inserted into the insertion hole 33, the elastic portion 48 is elastically deformed and urges the engagement protrusion 34 from both circumferential sides toward the circumferential center (as indicated by the arrow in FIG. 13). reference).

In this way, by providing the elastic member 46, no gap is created in the circumferential direction between the inner surface of the insertion hole 33 and the engagement protrusion 34 (see FIGS. 12 and 13), so the two-way clutch 2 is locked. It is possible to prevent wobbling in the circumferential direction from occurring when

The embodiments disclosed this time should be considered to be illustrative in all respects and not restrictive. The scope of the present invention is indicated by the claims rather than the above description, and it is intended that all changes within the meaning and range equivalent to the claims are included.

2 Two-way clutch 3 Electromagnetic clutch 4 Case 5 Input shaft 6 Output shaft 8 Inner ring 9 Outer ring 10 Engagement element (roller)
11 Retainer 12 Centering spring 23 Electromagnet 24 Armature 25 Friction plate 26 Separation spring 27 Inner cylinder part 28 Outer cylinder part 29 Field core 30 Solenoid coil 33 Insertion hole 34 Engagement protrusion 35 Biasing member 37 First engagement part 38 Second Engaging part 46 Elastic member 47 Fixing part 48 Elastic part

Claims (11)

a two-way clutch (2) that switches between transmitting and interrupting rotation between the input shaft (5) and the output shaft (6);
an electromagnetic clutch (3) that brakes the two-way clutch (2);
A rotation transmission device comprising:
a first engaging portion (37) provided on a member that rotates around an axis together with one of the input shaft (5) and the output shaft (6) during operation of the two-way clutch (2);
a second engaging portion (38) provided on a member that rotates around the axis together with the other of the input shaft (5) or the output shaft (6);
When the input shaft (5) and the output shaft (6) rotate relative to each other during operation of the two-way clutch (2), the first engagement portion (37) and the second engagement portion A rotation transmission device characterized in that (38) is configured to engage in a circumferential direction. The two-way clutch (2) is
an inner ring (8) provided on one of the input shaft (5) or the output shaft (6);
The input shaft (5) or the output shaft (6) has an outer ring (9) provided on the other shaft than the shaft provided with the inner ring (8);
an engager (10) disposed between the outer circumference of the inner ring (8) and the inner circumference of the outer ring (9);
An engagement position in which the engaging element (10) is held and engaged with the outer periphery of the inner ring (8) and the inner periphery of the outer ring (9), and a release position in which the engaging element (10) is released from the engagement. a retainer (11) arranged to be movable in the circumferential direction between positions;
A centering spring (12) is fixed to the inner ring (8) and the retainer (11) so as to elastically hold the retainer (11) in the released position and rotate together with the inner ring (8). )and,
has
The electromagnetic clutch (3) is
A field core (29) having a C-shaped circumferential cross section, including a cylindrical inner cylinder part (27) and an outer cylinder part (28) having a larger diameter than the inner cylinder part (27); an electromagnet (23) having a solenoid coil (30) wound between the inner cylinder part (27) and the outer cylinder part (28) of 29);
an armature (24) that is arranged to face the open end of the field core (29) from the axial direction and is attracted to the field core (29) when the electromagnet (23) is excited;
a friction plate (25) arranged to be movable in the axial direction while being prevented from rotating with respect to the retainer (11);
a separation spring (26) that urges the armature (24) toward the friction plate (25);
has
The second engaging portion (38) is attached to the axial end of the outer ring (9) facing the friction plate (25), and the friction plate (25) is provided with a biasing force of the separation spring (26). (25) is formed such that the first engaging portion (37) can engage with the second engaging portion (38) in the circumferential direction when the outer ring (9) presses the first engaging portion (37). The rotation transmission device according to item 1. The first engaging portion (37) is a protrusion extending outward from the outer edge of the friction plate (25), and the second engaging portion (38) is a protrusion extending outward from the outer edge of the outer ring (9). It is a protrusion extending outward from the first engaging part (37), at least one of the first engaging part (37) and the second engaging part (38) being bent in the axial direction to form the first engaging part (37). The rotation transmission device according to claim 2, wherein the second engaging portion (38) is engageable in the circumferential direction. The first engaging part (37) and the second engaging part (38) are formed at equal intervals in the circumferential direction, and the first engaging part (37) and the second engaging part The rotation transmission device according to claim 2 or 3, wherein the numbers of (38) are different. The rotation transmission device according to claim 2 or 3, wherein the inner ring (8) is provided with a biasing member (35) that biases the friction plate (25) in a direction toward the armature (24). An insertion hole (33) is formed in the friction plate (25), and an engagement protrusion (34) that is inserted into the insertion hole (33) is formed in the axial end of the retainer (11). The rotation transmission device according to claim 2 or 3, wherein the insertion hole (33) is provided with an elastic member (46) that biases the engagement protrusion (34) in the circumferential direction. The elastic member (46) is provided between a fixing portion (47) fixed to the friction plate (25) and the insertion hole (33), and the engagement portion inserted into the insertion hole (33). The rotation transmission device according to claim 6, further comprising an elastic portion (48) that urges the projection (34) toward the circumferential center of the insertion hole (33). a two-way clutch (2) that switches between transmitting and interrupting rotation between the input shaft (5) and the output shaft (6);
an electromagnetic clutch (3) that brakes the two-way clutch (2);
A rotation transmission device comprising:
an insertion hole (33) formed in a member that prevents rotation around the shaft during operation of the two-way clutch (2);
an engagement protrusion (34) formed on a member that rotates around the axis together with the input shaft (5) or the output shaft (6) and inserted into the insertion hole (33);
an elastic member (46) that biases the engagement protrusion (34) in the circumferential direction within the insertion hole (33);
A rotation transmission device characterized by having: The two-way clutch (2) is
an inner ring (8) provided on one of the input shaft (5) or the output shaft (6);
The input shaft (5) or the output shaft (6) has an outer ring (9) provided on the other shaft than the shaft provided with the inner ring (8);
an engager (10) disposed between the outer circumference of the inner ring (8) and the inner circumference of the outer ring (9);
An engagement position in which the engaging element (10) is held and engaged with the outer periphery of the inner ring (8) and the inner periphery of the outer ring (9), and a release position in which the engaging element (10) is released from the engagement. a retainer (11) arranged to be movable in the circumferential direction between positions;
A centering spring (12) is fixed to the inner ring (8) and the retainer (11) so as to elastically hold the retainer (11) in the released position and rotate together with the inner ring (8). )and,
has
The electromagnetic clutch (3) is
A field core (29) having a C-shaped circumferential cross section, including a cylindrical inner cylinder part (27) and an outer cylinder part (28) having a larger diameter than the inner cylinder part (27); an electromagnet (23) having a solenoid coil (30) wound between the inner cylinder part (27) and the outer cylinder part (28) of 29);
an armature (24) that is arranged to face the open end of the field core (29) from the axial direction and is attracted to the field core (29) when the electromagnet (23) is excited;
a friction plate (25) arranged to be movable in the axial direction while being prevented from rotating with respect to the retainer (11);
a separation spring (26) that urges the armature (24) toward the friction plate (25);
has
The rotating device according to claim 8, wherein the insertion hole (33) is formed in the friction plate (25), and the engagement protrusion (34) is formed at an axial end of the retainer (11). transmission device. The elastic member (46) is provided between a fixing portion (47) fixed to the friction plate (25) and the insertion hole (33), and the engagement portion inserted into the insertion hole (33). The rotation transmission device according to claim 9, further comprising an elastic portion (48) that urges the projection (34) toward the circumferential center of the insertion hole (33). The rotation transmission device according to claim 1 or 8, wherein the rotation transmission device is used as a clutch for connecting both shafts on the input shaft (5) side and the output shaft (6) side when a steer-by-wire device fails.

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